Channel selector valve and method of driving the same, compressor with the channel selector valve, and device for controlling refrigerating cycle

ABSTRACT

Upon a selector operation of a valve such as a four-way selector valve provided in a refrigerating cycle for selecting a channel of fluid, prevention of environmental pollution and energy saving and the like are effectively achieved. A sliding valve is coupled with a piston in a housing of a channel selector valve provided in a refrigerating cycle and the sliding valve moves due to a difference in pressure and so on at both sides of the piston, thereby a channel of fluid is selected. A processing section of a control device is constituted with microcomputers of an indoor and outdoor control sections, while a detecting section of the control device includes temperature sensor, detection means for detecting pressure, detection means for detecting flow rate, detection means for detecting voltage/current, and detection means for detecting frequency. Driving sections of an electrically-driven expansion valve, an indoor heat exchanger, an outdoor heat exchanger and a compressor are means that function in response to execution of control programs so that physical quantity, such as pressure, differential pressure and flow rate in the channel selector valve provided in the refrigerating cycle, and a rate of change in physical quantity, such as a rate of change in pressure, a rate of change in differential pressure and a rate of change in flow rate, are controlled, thereby a channel of the fluid is selected by the channel selector valve.

TECHNICAL FIELD

The present invention relates to a channel selector valve and, morespecifically, to a channel selector valve, which is used to reversechannels for fluid discharged from a compressor and for fluid suckedinto the compressor, and to a device for controlling a refrigeratingcycle.

BACKGROUND ART

In general, as to an air conditioner for both cooling and heating, afour-way selector valve selects a circulating direction of a refrigerantin such a manner that upon cooling the refrigerant flows from acompressor, by way of an outdoor heat exchanger, a throttle valve and anindoor heat exchanger, then flows back to the compressor, and that uponheating the refrigerant flows from a compressor, by way of an indoorheat exchanger, a throttle valve and an outdoor heat exchanger, thenflows back to the compressor.

The four-way selector valve, used for selecting a circulating directionof a refrigerant in a refrigerating cycle described above, includes theso-called sliding-type four-way selector valve.

As to the sliding-type four-way selector valve, a valve element is movedinside the valve housing so that one port, communicating with an inletthrough a space formed inside the valve element, is switched from afirst port to a second port out of the two ports and simultaneously thatanother port, communicating with an outlet through a space formedoutside the valve element, is switched from the second port to the firstport out of the two ports.

As disclosed, for example, in Japanese Patent Publication No. S35-12689and Japanese Utility Model Publication No. S55-53825, as to aconventional four-way selector valve, a magnet coil formed outside ofthe valve housing is provided with electricity so as to selectivelydecompress either valve chamber between two valve chambers disposed atboth sides of a central valve chamber, out of three valve chambers inthe valve housing, then the valve element placed in the central valvechamber is slided due to the differential pressure generated between thedecompressed valve chamber and the central valve chamber.

In Japanese Patent Publication No. H7-99296, there is disclosed afive-way valve, in which a valve element in a valve chamber is slidedwith the aid of a plunger of a magnet coil inserted in a valve housing,with supplying electricity to the magnet coil disposed outside the valvehousing.

As a conventional art similar to the above four or five-way valve, inJapanese Utility Model Laid-Open No. S58-42465, there is disclosed afour-way selector valve, in which with supplying electricity to heatersin operation chambers formed both sides of a valve housing, twooperation rods, each inserted from the respective operation chamber intothe valve housing, are alternately slided so that a valve element in thevalve housing is slided. Every conventional four or five-way valvementioned above needs electricity to be supplied to a magnet coil uponselecting by the valve, consequently, there has been a room forimprovement in these valves from the viewpoints of prevention of theenvironmental pollution and energy saving.

Besides the four or five-way valves, for example, in Japanese UtilityModel Laid-Open No. H3-119689, there is disclosed a four-way selectorvalve, in which wax thermoelements are disposed at both sides of a valvehousing instead of a magnet coil, and with supplying electricity toheaters of the wax thermoelements, a valve element in the valve housingis slided with the aid of a shaft, inserted from the outside of thevalve housing into the inside thereof.

In Japanese Patent No. 2757997, there is disclosed a four-way selectorvalve, in which a pair of differential pressure chambers partitioned bypartition wall plates is formed at respective sides of a valve chamberin a valve housing so that each differential pressure chamber canselectively communicate with the valve chamber by switching a substitutevalve formed on the respective partition wall plate, and aconstant-temperature heater of each slow operation element disposed atboth sides of the valve housing is supplied with electricity so thateach operation shaft inserted from the respective side of the valvehousing into the respective differential pressure chamber is slided. Inthis four-way selector valve, the constant-temperature heater of eachslow operation element is supplied with electricity so as to slide eachoperation shaft and to open either substitute valve, thereby bothpartition wall plates slide within the valve housing together with thevalve element in such a manner that the partition wall plates movenearer to the opened substitute valve.

Each conventional four-way selector valve mentioned above does notemploy a magnet coil, however, needs electricity to be supplied to theheaters in order to operate the switching valve, consequently, there hasbeen a room for improvement in these valves similarly to theaforementioned conventional four or five-way valve.

On the other hand, as to a four-way selector valve disclosed in JapanesePatent Publication No. H7-43188, although a valve element is slided bysupplying electricity to a magnet coil, a permanent magnet attracts theslided valve element so that a position of the valve element aftersupplying electricity is maintained, thereby saving a further supply ofelectricity to the magnet coil, then only a tentative electrical supplyis performed to another magnet coil for demagnetization when the valveelement is moved from the slided position back to an original positionbefore the slide.

As to a four-way selector valve disclosed in Japanese Patent ApplicationLaid-Open No. H9-72633, a position of a valve element after slide ismaintained by an intermittent electrical supply to a magnet coil, in thefour-way selector valve that is similar to one described in JapanesePatent Publication No. S35-12689.

Since each four-way selector valve, disclosed in Japanese PatentPublication No. H7-43188 or Japanese Patent Application Laid-Open No.H9-72633, does not need a continuous electrical supply to the magnetcoil, it has some effect from the viewpoints of prevention of theenvironmental pollution and energy saving.

Certainly, the four-way selector valve, disclosed in Japanese PatentPublication No. H7-43188 or Japanese Patent Application Laid-Open No.H9-72633, restricts an amount of electrical supply to the magnet coil,however, it still needs some amount of electrical supply. Therefore,from the viewpoints of a vigorous promotion with respect to preventionof the environmental pollution and energy saving, there has been a roomfor further improvement in the valves described above.

Therefore, as to a selecting operation of a channel selector valve forfluid, such as a four-way selector valve, which is provided in arefrigerating cycle, it is an objective of the present invention tosolve the above problems and to provide a channel selector valve thatcan effectively contribute for prevention of the environmental pollutionand energy saving, a method of driving the channel selector valve, acompressor that works excellently with using the channel selector valve,and a device for controlling a refrigerating cycle.

DISCLOSURE OF INVENTION

In order to attain the above objective, embodiments of the presentinvention relate to a channel selector valve, a method of driving thechannel selector valve, a compressor with the channel selector valve,and a device for controlling a refrigerating cycle.

The present invention provides a channel selector valve for selecting achannel of fluid characterized in that the channel is selected byemploying non-electric motive power generated when a control sectioncontrols a physical quantity of the fluid.

According to one embodiment of the present invention a drive sourceprovided separately from the channel selector valve generatesnon-electric motive power, by which the channel is passively selected.

According to another embodiment of the present invention the drivesource comprises at least one of element components in a refrigeratingcycle having a channel selector valve and the channel is passivelyselected by using the motive power generated by said at least one of theelement components.

According to a further embodiment of the present invention the motivepower is generated due to a change in physical quantity, which arises inthe refrigerating cycle from an action of said at least one of theelement components.

According to a further embodiment of the present invention the change inphysical quantity is at least one change among changes in pressure,differential pressure and flow rate of fluid in the channel selectorvalve, said changes arising from an action of said at least one of theelement components.

The present invention further provides a channel selector valvecomprising: a movable member moving between a first position and asecond position in a housing of the channel selector valve; and drivingmeans for driving the movable member between the first position and thesecond position by employing non-electric motive power generated when acontrol section controls a physical quantity of the fluid, wherein afirst selector port out of two selector ports of the housingcommunicates with a main port of the housing through the interior of thehousing when the movable member is situated at the first position, whilea second selector port out of the two selector ports of the housingcommunicates with a main port of the housing through the interior of thehousing when the movable member is situated at the second position.

According to one embodiment of the present invention a drive sourcegenerating a non-electric motive power comprises at least one of elementcomponents in a refrigerating cycle having the channel selector valve, achange in physical quantity, which arises in the refrigerating cyclefrom an action of said at least one of element components, is employedas at least a part of said motive power, thereby the channel ispassively selected.

According to a further embodiment of the present invention the change inphysical quantity is at least one change among changes in pressure,differential pressure and flow rate of fluid in the channel selectorvalve, said changes arising from an action of said at least one of theelement components.

The present invention further provides a channel selector valveconstituted as a four-way selector valve by combining first and secondthree-way selector valves, each of which is constituted by a channelselector valve.

According to one embodiment of the present invention the channelselector valve is constituted as a four-way selector valve by the firstand second three-way selector valves in which,

the main port of the first three-way selector valve is an inlet portformed in the housing, through which fluid introduced from the exteriorto the interior of the housing of the first three-way selector valvepasses, while the main port of the second three-way selector valve is anoutlet port formed in the housing, through which the fluid dischargedfrom the interior to the exterior of the housing of the second three-wayselector valve passes,

the first selector port of the first three-way selector valve isconnected to the second selector port of the second three-way selectorvalve, while the second selector port of the first three-way selectorvalve is connected to the first selector port of the second three-wayselector valve,

the movable member of the second three-way selector valve moves to thesecond position when the movable member of the first three-way selectorvalve moves to the first position, while the movable member of thesecond three-way selector valve moves to the first position when themovable member of the first three-way selector valve moves to the secondposition.

According to another embodiment of the present invention the drivingmeans of a first three-way selector valve comprises:

a first drive mechanism that moves the movable member situated at thefirst position of the first three-way selector valve to the secondposition when a difference between a fluid pressure at the firstselector port in the first three-way selector valve and a fluid pressureat the second selector port cancels out; and

a second drive mechanism that moves the movable member situated at thesecond position of the first three-way selector valve to the firstposition when a difference between a fluid pressure at the firstselector port in the first three-way selector valve and a fluid pressureat the second selector port cancels out.

According to a further embodiment of the present invention first andsecond three-way selector valves are constructed so that the main portis isolated from the second selector port when a movable member issituated between a first position and a third position where it isnearer to a second position than the first position, while that the mainport is isolated from the first selector port when the movable member issituated between the second position and a fourth position where isbetween the second position and the third position,

a first drive mechanism comprises first storing means for storingenergizing force to move the movable member of the first three-wayselector valve from the first position to the fourth position, by afluid pressure being higher than a first predetermined value of the mainport, when the movable member of the first three-way selector valve issituated at the first position, said energizing force being less thanthe first predetermined value, and

a second drive mechanism comprises second storing means for storingenergizing force to move the movable member of the first three-wayselector valve from the second position to the third position, by afluid pressure being higher than a second predetermined value of themain port, when the movable member of the first three-way selector valveis situated at the second position, said energizing force being lessthan the second predetermined value.

According to a further embodiment of the present invention a main portis an inlet port formed in the housing, through which fluid introducedfrom the exterior to the interior of the housing passes,

the housing further comprises an outlet port, through which the fluiddischarged from the interior to the exterior of the housing passes,

when a movable member is situated at a first position, an inlet port anda first selector port are communicated with each other inside thehousing, while an outlet port and a second selector port arecommunicated with each other inside the housing,

when the movable member is situated at a second position, the inlet portand the second selector port are communicated with each other inside thehousing, while the outlet port and the first selector port arecommunicated with each other inside the housing.

According to another embodiment of the present invention a movablemember partitions the interior of the housing into a first and secondpressure chambers and also forms first and second spaces in the firstpressure chamber,

an inlet port is formed in the housing so as to communicate with thefirst space and an outlet port is formed in the housing so as tocommunicate with the second space,

when the movable member is situated at a first position, fluidintroduced from the exterior of the housing into the first space by wayof the inlet port is discharged to a first selector port, while thefluid discharged from the second space to the exterior of the housing byway of the outlet port is introduced from a second selector port,

when the movable member is situated at a second position, the fluidintroduced from the exterior of the housing into the first space by wayof the inlet port is discharged to the second selector port, while thefluid discharged from the second space to the exterior of the housing byway of the outlet port is introduced from the first selector port.

The present invention further provides a method of driving a channelselector valve as described above which comprises the steps of:

communicating the first space to the second pressure chamber through anequalizing path formed in the movable member;

energizing the movable member in a direction of moving from the secondposition to the first position by energizing means for energizing; and

applying a force to the movable member from the first pressure chamberside by fluid introduced from the exterior of the housing into the firstspace by way of the inlet port, said force being stronger than aresultant force consisting of an energizing force by said energizingmeans and a force applied to the movable member by fluid in the secondpressure chamber introduced from the first space by way of saidequalizing path,

thereby the movable member moves from the first position to the secondposition.

According to a further embodiment of the present invention a housing hasa valve seat disposed in a first pressure chamber, an outlet port andtwo selector ports are disposed on a valve seat, a second space moves onthe valve seat responding to a movement of a movable member movingbetween first and second positions, and a place with which the outletport communicates by way of the second space is selected to be eitherthe first selector port or the second selector port.

The present invention further provides a method of driving a channelselector valve as described above which comprises the steps of:

communicating a first space to a second pressure chamber through anequalizing path formed in a movable member;

energizing the movable member in a direction of moving from a secondposition to a first position by energizing means for energizing; and

applying a force to the movable member from a first pressure chamberside by fluid introduced from the exterior of the housing into the firstspace by way of an inlet port, said force being stronger than aresultant force consisting of an energizing force by said energizingmeans, a force applied to the movable member by fluid in the secondpressure chamber introduced from the first space by way of an equalizingpath, and a static friction force between a valve seat and the movablemember,

whereby the movable member moves from the first position to the secondposition and

the movable member is kept staying at the second position by the staticfriction force between the valve seat and the movable member against anenergizing force of the energizing means, after a difference between apressure of fluid in the first space and that in the second pressurechamber decreases due to circulation of fluid between the first spaceand the second pressure chamber through the equalizing path.

According to another embodiment of the present invention the drivingmeans comprises:

a third drive mechanism that moves a movable member from one positionout of a first and second positions toward an opposite position; and

a fourth drive mechanism that moves the movable member from the oppositeposition toward the one position,

wherein the third and fourth drive mechanisms employ a change inphysical quantity of the interior of the housing due to fluid introducedinto the interior of the housing at least as a part of the motive power.

According to a further embodiment of the present invention the channelselector valve includes a movable member that partitions the interior ofthe housing into a first pressure chamber, a second pressure chamber,and a third pressure chamber situated so that the first pressure chamberis sandwiched between the second and third pressure chambers,

the channel selector valve further comprises a non-electrically-drivenpilot valve that selectively communicates an outlet port to either thesecond pressure chamber or the third pressure chamber, said pilot valvecomprises:

a second housing having a second main port that is provided outside thehousing and communicates with the outlet port; and

a selector valve element that partitions the interior of a secondhousing into a fourth pressure chamber communicating with the thirdpressure chamber and a fifth pressure chamber communicating with thesecond pressure chamber, and that is movable in the second housingbetween a fifth position where the second main port communicates withthe fourth pressure chamber and a sixth position where the second mainport communicates with the fifth pressure chamber, due to a differencebetween a pressure of fluid in the second pressure chamber and that inthe third pressure chamber.

According to another embodiment, the present invention further comprisessecond driving means to move a selector valve element from one positionout of fifth and sixth positions to an opposite position when thedifference between a pressure of fluid in a second pressure chamber andthat in a third pressure chamber cancels out.

According to a still further embodiment of the present invention amovable member has a first equalizing path communicating a first spaceto a second pressure chamber and a second equalizing path communicatingthe first space to a third pressure chamber,

the movable member has a first subvalve that isolates the third pressurechamber from a fourth pressure chamber when the movable member issituated at a first position and that communicates the third pressurechamber to the fourth pressure chamber when the movable member issituated at a second position, and has a second subvalve thatcommunicates the second pressure chamber to a fifth pressure chamberwhen the movable member is situated at the first position and thatisolates the second pressure chamber from the fifth pressure chamberwhen the movable member is situated at the second position,

a pilot valve communicates a second main port to the fourth pressurechamber when the selector valve element is situated between a fifthposition and a seventh position located nearer to a sixth position thanthe fifth position, and communicates the second main port to the fifthpressure chamber when the selector valve element is situated between thesixth position and an eighth position located between the sixth positionand the seventh position, and

a second driving means has third and fourth storing means for storingenergizing force,

the third storing means for storing energizing force stores anenergizing force, which is less than a third predetermined value, tomove the selector valve element from the fifth position to the eighthposition due to a fluid pressure in the fifth pressure chamber exceedingthe third predetermined value when the selector valve element issituated at the fifth position, and

the fourth storing means for storing energizing force stores anenergizing force, which is less than a fourth predetermined value, tomove the selector valve element from the sixth position to the seventhposition due to a fluid pressure in the fourth pressure chamberexceeding the fourth predetermined value when the selector valve elementis situated at the sixth position.

According to a yet further embodiment, the present invention comprises:

a third main port communicating with an inlet port is further formed ina second housing,

the third main port communicates with a fifth pressure chamber when theselector valve element is situated between the fifth and seventhpositions and communicates with a fourth pressure chamber when theselector valve element is situated between sixth and eighth positions,

and the channel selector valve further comprises second driving meansfor moving the selector valve element either from the fifth position tothe eighth position or from the sixth position to the seventh positionwhen the difference between a pressure of fluid in a second pressurechamber and that in a third pressure chamber cancels out.

According to another embodiment of the present invention in which thesecond driving means has third and fourth storing means for storingenergizing force,

the third storing means for storing energizing force stores anenergizing force, which is less than a third predetermined value, tomove the selector valve element from a fifth position to an eighthposition due to a fluid pressure in a fifth pressure chamber exceeding athird predetermined value when the selector valve element is situated ata fifth position, and

the fourth storing means for storing energizing force stores anenergizing force, which is less than a fourth predetermined value, tomove the selector valve element from a sixth position to a seventhposition due to a fluid pressure in a fourth pressure chamber exceedingthe fourth predetermined value when the selector valve element issituated at the sixth position.

According to a further embodiment of the present invention the drivingmeans comprises:

a third drive mechanism to move a movable member from one position outof first and second positions to an opposite position; and

a fourth drive mechanism to move the movable member from the oppositeposition to the one position,

wherein one drive mechanism out of third and fourth drive mechanismsemploys a change in physical quantity of the interior of the housing dueto fluid introduced into the interior of the housing at least as a partof the motive power, while an opposite drive mechanism employs anenergizing force that is applied to the movable member by energizingmeans received in the interior of the housing at least as a part of themotive power.

A still further embodiment of the present invention comprises a latchmechanism that selectively controls a movement of a movable member fromone position out of first and second positions toward an oppositeposition.

According to a further embodiment of the present invention a latchmechanism selectively performs a first and second states,

in the first state, a movement of a movable member to an oppositeposition by a driving means is controlled at a first position, and

in the second state, a movement of the movable member from the oneposition to the opposite position by the driving means is allowed.

According to another embodiment of the present invention a latchmechanism comprises a latch piece that moves in the housing following amovement of a movable member between first and second positions, and ina first state of the latch mechanism, a movement of the latch piece iscontrolled, thereby a movement of the movable member is controlled atthe one position.

The present invention further provides a method of driving a channelselector valve wherein

when a movable member, a movement of which to an opposite position iscontrolled by a latch mechanism and situated at one position, is movedto an opposite position, the movable member is once moved by a drivingmeans in a direction of moving from the opposite position to the oneposition, then is moved from the one position to the opposite position,

and when the movable member situated at the opposite position is movedto the one position, the movable member is once moved by the drivingmeans in a direction of moving from the one position to the oppositeposition, then is moved from the opposite position to the one position.

According to another embodiment of the present invention the channelselector valve further comprises:

a valve-opening member that moves from a valve-closing position to avalve-opening position by the motive power while a third drive mechanismgenerates the motive power;

a pilot path that is opened from a valve closing state thereof by thevalve-opening member moved from the valve-closing position to thevalve-opening position;

an attenuation mechanism acting when the pilot path is open, whichattenuates the motive power generated by a fourth drive mechanism so asto prevent the movable member from moving from the opposite position tothe one position; and

a second latch mechanism to selectively control a movement of thevalve-opening member from the valve-closing position to thevalve-opening position.

According to a further embodiment of the present invention as describedin a second latch mechanism alternately repeats a third and fourthstates,

in the third state, a movement of the valve-opening member to avalve-opening position is controlled at a valve-closing position, and

in the fourth state, a movement of the valve-opening member from thevalve-closing position to the valve-opening position is allowed.

The present invention further provides a method of driving a channelselector valve as described above wherein

when a movable member situated at one position is moved to an oppositeposition, a generation of the motive power by a third drive mechanism isonce halted, then the generation thereof by the third drive mechanism isstarted again and then, the motive power generated by the third drivemechanism is maintained to be a predetermined value exceeding the motivepower, which is generated by the fourth drive mechanism and attenuatedby the attenuation mechanism,

and when the movable member situated at the opposite position is movedto the one position, a generation of the motive power by the third drivemechanism is halted, then the movable member is moved from the oppositeposition to the one position by the fourth drive mechanism.

According to a still further embodiment of the present invention adriving means comprises a communication pipe that always communicates asecond pressure chamber to a first selector port outside the housing.

According to a yet further embodiment of the present invention a drivingmeans comprises a state-holding mechanism to hold a movable member,which is moved from a first position to a second position, at the secondposition.

According to a further embodiment of the present invention astate-holding mechanism comprises:

a state-holding selector valve provided in a second pressure chamber,which by a selecting action of a second selector valve element selectseither a first state or a second state, in said first state the secondpressure chamber communicates with the exterior of the housing through afirst introducing port and in said second state the second pressurechamber communicates with the exterior of the housing through a secondintroducing port; and

energizing means for energizing the selector valve, which energizes thesecond selector valve element so that the state-holding selector valvein the second state selects the first state,

a movable member allows the energizing means for energizing the selectorvalve to energize the second selector valve element when the movablemember is situated at a first position, while the movable member makesthe second selector valve element act a selection so that thestate-holding selector valve selects the second state against anenergizing by the energizing means for energizing the selector valvewhen the movable member is situated at a second position.

According to a further embodiment of the present invention an energizingmeans energizes a movable member in a direction of moving from a secondposition to a first position, and a pressure of fluid, which isintroduced from the exterior of the housing into a first space by way ofan inlet port, acts on the movable member in a direction of moving fromthe first position to the second position.

The present invention also provides a method of driving a channelselector valve as described above wherein

when a movable member moves from a first position to a second position,a pressure of fluid introduced into a first space from the exterior ofthe housing by way of an inlet port is set higher than a predeterminedvalue, so that a force, which is applied to the movable member by fluidexisting in the first space in a direction from the first position tothe second position, is set stronger than a force, which is applied tothe movable member by fluid existing in the place to which a secondpressure chamber is communicated in a direction from the second positionto the first position,

after the movable member has moved from the first position to the secondposition, a pressure of fluid existing in the first space and a pressureof fluid existing in the second pressure chamber are set so that themovable member is kept staying at the second position.

According to another embodiment of the present invention the elementcomponent described above is an electrically-driven expansion valveprovided in the refrigerating cycle and the change in physical quantityis a change in pressure of fluid due to a change in an opening ratio ofthe electrically-driven expansion valve.

According to a further embodiment of the present invention the elementcomponent described above is a compressor provided in the refrigeratingcycle and the change in physical quantity is a change in a frequency ofa mechanical oscillation generated by the compressor.

According to a still further embodiment of the present invention theelement component described above is a heat exchanger provided in therefrigerating cycle and the change in physical quantity is a change inpressure of fluid due to a change in the amount of heat exchange by theheat exchanger.

According to a further embodiment of the present invention the housingis cylindrical,

at least two selector ports are formed at a valve seat situated at oneend of the housing in a direction of a central axis of the housing,

a movable member is constructed by a main valve element, which isreceived in the housing and rotative around the central axis,

the main valve element is provided with communication means forselectively communicating a selector port out of the two selector portsto the main port,

the main valve element rotates and displaces around the central axis soas to move between first and second positions, when the main valveelement is situated at the first position, a first selector port out ofthe two selector ports is communicated to the main port by thecommunication means, and when the main valve element is situated at thesecond position, a second selector port out of the two selector ports iscommunicated to the main port by the communication means.

According to a still further embodiment of the present invention

at least one port out of an inlet port and an outlet port is formed at avalve seat,

an end surface of a main valve element in a direction of a central axissits down on the valve seat,

said end surface is provided with second communication means forselectively communicating said one port to a first selector port out ofthe two selector ports,

when the main valve element is situated at the first position, thesecond communication means communicates the second selector port to saidone port, and when the main valve element is situated at the secondposition, the second communication means communicates the first selectorport to said one port.

According to a yet further embodiment of the present invention anopposite port is formed at an opposite end of the housing in a directionof the central axis, and a communication means has a communicationchannel that communicates one end surface side of a main valve elementto an opposite end surface side of the main valve element in theinterior of the housing.

According to a still further embodiment, the present invention furthercomprises conversion means for converting a moving direction, whichconverts a movement of a main valve element in a direction of a centralaxis with respect to the housing into a movement in a rotationaldirection around the central axis, wherein the main valve element ismovable in a direction of the central axis in the interior of thehousing, and a driving means makes the main valve element have areciprocating motion in a direction of the central axis with respect tothe housing.

According to one embodiment of the present invention

a conversion means for converting a moving direction comprises:

a cam groove that is provided in one of a main valve element and ahousing, and extends over a whole circumference of a rotationaldirection; and

a cam follower pin that is provided in another out of the main valveelement and the housing, and moves in a cam groove,

the cam groove has a first and second cam grooves continuing with eachother in the rotational direction, said first cam groove is formedinclined so as to part from the valve seat in a direction of the centralaxis as being displaced in the rotational direction, while said secondcam groove is formed inclined so as to move nearer to the valve seat ina direction of the central axis as being displaced in the rotationaldirection.

According to another embodiment of the present invention

a cam groove is provided in the housing,

the housing comprises an outer housing and an inner housing received inthe outer housing,

the inner housing comprises a first half and a second half divided in adirection of the central axis in a state that the inner housing isreceived in the outer housing, and

each guide, which constitutes the cam groove in a state that an end ofthe first half and an end of the second half are joined with each other,is formed at the respective ends of the first and second halves.

According to another embodiment of the present invention

at least one port out of an inlet port and an outlet port is formed atthe valve seat,

second communication means is formed at an end surface of a main valveelement, the end surface faces the valve seat, said second communicationmeans selectively communicates the opposite port to a first selectorport out of two selector ports in a state that the end surface sits downon the valve seat,

when the main valve element is situated at a first position, the secondselector port is communicated to the opposite port by the secondcommunication means of the main valve element, and the end surface ofwhich sits down on the valve seat, and

when the main valve element is situated at a second position, the firstselector port is communicated to the opposite port by the secondcommunication means of the main valve element, and the end surface ofwhich sits down on the valve seat.

According to a still further embodiment of the present invention inwhich the opposite port is formed at an opposite end side of the housingin a direction of the central axis, and the communication meanscomprises:

a communication channel that communicates one end surface side of themain valve element to an opposite end surface side of the main valveelement in the housing;

a subvalve that opens and closes the communication channel;

subvalve energizing means for energizing the subvalve toward a directionof closing; and

valve opening means for opening the subvalve against an energizing forceby the subvalve energizing means in a state that the one end surface ofthe main valve element sits down on the valve seat.

According to a still further embodiment of the present invention thehousing is disposed so that the opposite end of the housing is situatedlower than one end of the housing in a direction of the central axis,and a driving means employs an own weight of a main valve element atleast as a part of the motive power.

According to a yet further embodiment of the present invention a drivingmeans employs an energizing force by energizing means for energizing amain valve element, which energizes the main valve element to part froma valve seat in a direction of a central axis, as a part of the motivepower.

According to another embodiment of the present invention a driving meanscomprises second energizing means for energizing a main valve element,which energizes the main valve element to move nearer to a valve seat ina direction of a central axis.

According to a further embodiment of the present invention a drivingmeans comprises energizing means for energizing a main valve element,which energizes the main valve element to part from a valve seat in adirection of a central axis, due to a resultant force of an energizingforce by a energizing means for energizing the main valve element and anenergizing force by a second energizing means for energizing the mainvalve element, a cam follower pin is situated at an intermediateposition of a cam groove except end portions of one end side and anopposite end side of the housing in a direction of the central axis, andthe main valve element is situated at a neutral position halfway withina reciprocating motion in a direction of the central axis when the camfollower pin is situated at the intermediate position.

According to a further embodiment of the present invention

an end portion of one end side of the housing in a direction of acentral axis a cam groove is provided with a groove that continues to ajoin, at which one end of a first cam groove being situated at the oneend side of the housing is connected to one end of a second cam groove,

the groove is formed so that one end surface of the main valve elementsits down on a valve seat in a state that the cam follower pin issituated at the groove,

the groove is disposed being displaced to a lower course than the joinin the rotational direction, and

when the main valve element moves in the direction away from the valveseat in a direction of the central axis, a movement of the cam followerpin is controlled from the groove to a cam groove out of the first andsecond cam grooves, which is situated at the upper course than thegroove in the rotational direction.

According to another embodiment of the present invention

an end portion of an opposite end side of a housing in a direction of acentral axis out of a cam groove is provided with a second groove thatcontinues to a join, at which an opposite end of a first cam groovebeing situated at the opposite end side of the housing is connected toan opposite end of the second cam groove,

the second groove is formed so that a main valve element is the farthestaway from a valve seat in a state that the cam follower pin is situatedat the second groove,

the second groove is disposed being displaced to the lower course than asecond join in the rotational direction, and

when the main valve element moves in the direction nearer to the valveseat in a direction of the central axis, a movement of the cam followerpin is controlled from the second groove to a cam groove out of thefirst and second cam grooves, which is situated at the upper course thanthe second groove in the rotational direction.

According to another embodiment of the present invention slide means fordecreasing a sliding resistance between the housing and a main valveelement is provided therebetween.

The present invention further provides a compressor with a channelselector valve as described above comprises:

a compressor housing having an inlet, which is connected to the outletport;

a low pressure chamber that is provided in the interior of thecompressor housing and communicates with the inlet;

a high pressure chamber that is provided in the interior of thecompressor housing and partitioned off from the low pressure chamber;and

a compressing section that is provided in the interior of the compressorhousing, compresses fluid introduced into the low pressure chamber fromthe inlet, and guides the fluid into the high pressure chamber,

wherein a part of the compressor housing partitioning the high pressurehousing therein is integrally formed with a part of the housing havingthe inlet port therein, thereby the interior of the part of the housingcommunicates with the high pressure chamber.

The present invention further provides a device for controlling arefrigerating cycle which controls a channel selector valve communicatedto the refrigerating cycle, characterized in that:

the device controls at least one of a plurality of functional componentscommunicated to the refrigerating cycle so as to control therefrigerating cycle; and

the device controls the channel selector valve by controlling thefunctional components.

The present invention further provides a device for controlling arefrigerating cycle which controls a channel selector valve communicatedto the refrigerating cycle, characterized in that:

the device controls at least one of a plurality of functional componentscommunicated to the refrigerating cycle so as to control therefrigerating cycle; and

the device generates a non-electrical motive power by controlling thefunctional components and passively controls the channel selector valveby employing the motive power.

The present invention further provides a device for controlling arefrigerating cycle which controls a channel selector valve communicatedto the refrigerating cycle, comprising:

a microcomputer that controls at least one of a plurality of functionalcomponents communicated to the refrigerating cycle so as to control therefrigerating cycle; and

a control program, by which the microcomputer performs a processing thatcontrols the functional components so as to generate a non-electricalmotive power for passively controlling the channel selector valve.

The present invention also provides a device for controlling arefrigerating cycle which controls a channel selector valve communicatedto the refrigerating cycle, characterized in that:

the device controls at least one of a plurality of functional componentscommunicated to the refrigerating cycle so as to control therefrigerating cycle;

the non-electrical motive power generated by controlling the functionalcomponents is a physical quantity or a rate of change in a physicalquantity generated by the refrigerating cycle; and

the device passively controls the channel selector valve by the physicalquantity or the rate of change in a physical quantity.

The present invention also provides a device for controlling arefrigerating cycle which controls a channel selector valve communicatedto the refrigerating cycle, comprising:

a microcomputer that controls at least one of a plurality of functionalcomponents communicated to the refrigerating cycle so as to control therefrigerating cycle; and

a control program, by which the microcomputer performs a processing thatcontrols the functional components so as to allow the refrigeratingcycle to generate a physical quantity or a rate of change in a physicalquantity as a non-electrical motive power for passively controlling thechannel selector valve.

The present invention further provides a device for controlling arefrigerating cycle wherein a physical quantity, which is a base forcontrolling functional components to generate the non-electrical motivepower, is a parameter selected from the group consisting of a pressure,temperature, rate of flow, voltage, current, electrical frequency andmechanical oscillation frequency with respect to a control of therefrigerating cycle.

The present invention further provides a device for controlling arefrigerating cycle wherein

a physical quantity, which is the non-electrical motive power and isgenerated by the refrigerating cycle, is a pressure, differentialpressure or rate of flow with respect to fluid existing in the channelselector valve, and

the rate of change in a physical quantity, which is the non-electricalmotive power and is generated by the refrigerating cycle, is a rate ofchange in pressure, rate of change in differential pressure or rate ofchange in rate of flow with respect to the fluid.

The present invention further provides a device for controlling arefrigerating cycle which controls a channel selector valve communicatedto the refrigerating cycle, comprising a control section that receivesinput signals sent from an operation command section for commanding anoperational condition of the refrigerating cycle and a physical quantitydetector section for detecting a physical quantity generated by therefrigerating cycle,

wherein the control section sends output signals to a driving sectionthat drives a drive source of at least one of a plurality of functionalcomponents communicated to the refrigerating cycle so as to control saidfunctional component, and the device generates a non-electrical motivepower by controlling the refrigerating cycle and passively controls thechannel selector valve by the motive power.

The present invention also provides a device for controlling arefrigerating cycle wherein a control section controls at least one of aplurality of functional components communicated to the refrigeratingcycle so as to start an operation of the refrigerating cycle, therebycontrolling a channel selector valve in a state corresponding to thestart of an operation, which is commanded by the operation commandsection.

The present invention also provides a device for controlling arefrigerating cycle wherein a control section starts to operate acompressor communicated to the refrigerating cycle in a direction ofinverse rotation when the control section decides to select a channelselector valve on the basis of a command of the operation commandsection.

The present invention also provides a device for controlling arefrigerating cycle wherein a control section controls at least one of aplurality of functional components communicated to the refrigeratingcycle so as to operate the refrigerating cycle, thereby controlling achannel selector valve in a state corresponding to the operation, whichis commanded by the operation command section.

The present invention further provides a device for controlling arefrigerating cycle wherein a control section controls at least one of aplurality of functional components communicated to the refrigeratingcycle so as to halt an operation of the refrigerating cycle, therebycontrolling a channel selector valve in a state corresponding to thehalt of the operation, which is commanded by the operation commandsection.

The present invention further provides a device for controlling arefrigerating cycle wherein a channel selector valve is constructed in amanner that a movable member moves so as to select a channel, and thecontrol section comprises at least one unit selected from the groupconsisting of: a memory unit for memorizing position data of the movablemember of the channel selector valve; a comparison unit and a judge unitfor comparing and judging, respectively, the position data and operationcommand data; and a learning unit learning on the basis of physicalquantity data by a control of functional components and control data ofa channel selector valve.

The present invention also provides a device for controlling arefrigerating cycle wherein a control section receives input signals,performs a predetermined processing and judges whether a channel is tobe changed or not to be changed by a channel selector valve,

then confirms a position on the basis of present position data,

then sends the output signals to a driving section so as to control thefunctional components in the refrigerating cycle,

then receives new input signals after a predetermined period of time,confirms a position of a movable member, and sets position data of saidposition as new present position data when said position is changed to anew position.

The present invention also provides a device for controlling arefrigerating cycle wherein a control section confirms a position of amovable member by at least one temperature detection means for detectingtemperature, at least one pressure detection means for detectingpressure, at least one magnetism detection means for detectingmagnetism, at least one current detection means for detecting current ora combination thereof after a predetermined period of time, and theninstalls position data corresponding to said position into a memory unitof the control section.

The present invention further provides a device for controlling arefrigerating cycle which controls a channel selector valve that iscommunicated to a refrigerating cycle and selects a channel by amovement of a movable member, which device comprises:

a microcomputer that controls at least one of a plurality of functionalcomponents communicated to the refrigerating cycle so as to control therefrigerating cycle; and

a control program, by which the microcomputer performs a processingconsisting of the steps of:

receiving input signals;

confirming a position by taking out present position data of a movablemember installed in a memory unit;

carrying out an operation to decide whether the movable member is to bemoved of not to be moved, comparing, and judging;

selecting and deciding a driving section;

outputting drive signals to the driving section selected and decided;

judging a position of the movable member by input signals after apredetermined period of time, with or without moving a position of themovable member by a physical quantity generated by at least onefunctional component that is selected and decided in said step ofselecting and deciding or a rate of the physical quantity; and

installing position data of a position of the movable member into thememory unit when said position is changed to a new position,

in order to control the driving section for driving the functionalcomponent so that the position of the movable member is to be moved ornot to be moved.

The present invention further provides a device for controlling arefrigerating cycle which controls a channel selector valve communicatedto the refrigerating cycle, which device comprises:

a control section that receives input signals sent from an operationcommand section for commanding an operation state of the refrigeratingcycle and from a physical quantity detector section for detecting aphysical quantity generated by the refrigerating cycle,

wherein the control section sends output signals to a driving sectionthat drives a drive source of at least one of a plurality of functionalcomponents communicated to the refrigerating cycle so as to control saidfunctional component and to control the refrigerating cycle, and whenjudging to select a channel by using the channel selector valve on thebasis of a command of the operation command section, the control sectionsends output signals to a driving section for driving a power source ofa compressor so as to start an operation of the compressor of therefrigerating cycle and starts an operation of the refrigerant cycle soas to generate a motive power exceeding a first predetermined motivepower, thereby a channel selector valve is passively controlled.

The present invention further provides a device for controlling arefrigerating cycle which controls a channel selector valve communicatedto the refrigerating cycle, which device comprises:

a control section that receives input signals sent from an operationcommand section for commanding an operation state of the refrigeratingcycle and from a physical quantity detector section for detecting aphysical quantity generated by the refrigerating cycle,

wherein the control section sends output signals to a driving sectionthat drives a drive source of at least one of a plurality of functionalcomponents communicated to the refrigerating cycle so as to control saidfunctional component and to control the refrigerating cycle, and whenjudging to select a channel by using the channel selector valve on thebasis of a command of the operation command section, the control sectionsends output signals to a driving section for driving a power source ofa compressor so as to start an operation of the compressor in adirection of inverse rotation and starts an operation of the refrigerantcycle so as to generate a motive power exceeding a third predeterminedmotive power, thereby a channel selector valve is passively controlled.

The present invention also provides a device for controlling arefrigerating cycle as described above wherein

a channel selector valve selects a channel by moving a movable memberbetween first and second positions in response to an internal motivepower,

a control section memorizes position data corresponding to the first orsecond position of the movable member in a memory unit thereof,

the control section starts an operation of the refrigerating cycle whenthe position data indicates the second or first position,

halts the operation of the refrigerating cycle with renewing positiondata in a memory unit to the first or second position, respectively,after a first predetermined period of time, and

keeps the operation of the refrigerating cycle standby during a thirdpredetermined period of time.

The present invention further provides a device for controlling arefrigerating cycle as described above wherein the control sectionoperates a compressor in a specific frequency immediately after startingthe operation of the compressor and starts an operation of therefrigerating cycle so that a motive power exceeding a firstpredetermined motive power is generated as an internal motive power ofthe channel selector valve.

The present invention also provides a device for controlling arefrigerating cycle as described above wherein the control sectionstarts an operation of the compressor with a first predeterminedcapacity.

The present invention further provides a device for controlling arefrigerating cycle as described above wherein the control sectionstarts an operation of the compressor with a second predeterminedcapacity so that a motive power lower than a first predetermined motivepower is generated as an internal motive power of the channel selectorvalve,

then operates the refrigerating cycle for a fourth predetermined periodof time,

then halts the operation of the refrigerating cycle for a fifthpredetermined period of time, and

then starts an operation of the compressor with a first predeterminedcapacity so that a motive power exceeding a first predetermined motivepower is generated as an internal motive power of the channel selectorvalve.

The present invention also provides a device for controlling arefrigerating cycle as described above wherein the control section sendsoutput signals to a throttle device driving section so that an openingratio of a throttle device of the refrigerating cycle is almost fullyopened or almost fully closed.

The present invention also provides a device for controlling arefrigerating cycle as described above wherein the control section sendsoutput signals to a heat exchanger motor driving section so that a heatexchanger motor of the refrigerating cycle is kept halted.

The present invention also provides a device for controlling arefrigerating cycle as described above wherein once the control sectionstarts an operation of the compressor, the control section sends outputsignals to the compressor driving section after a first predeterminedperiod of time and drives the power source of the compressor so that amotive power exceeding a second predetermined motive power is generated,thereby operating the refrigerating cycle.

The present invention further provides a device for controlling arefrigerating cycle as described above wherein once the control sectionstarts an operation of the compressor, the control section sends outputsignals to the throttle device driving section so as to set the openingratio of the throttle device a predetermined opening ratio after a firstpredetermined period of time.

The present invention further provides a device for controlling arefrigerating cycle as described above wherein once the control sectionstarts an operation of the compressor, the control section sends outputsignals to the heat exchanger motor driving section after a secondpredetermined period of time so as to start an operation of the heatexchanger motor, sends output signals to the compressor driving sectionso as to generate a motive power lower than a first predetermined motivepower, and drives the power source of the compressor so as to generate amotive power exceeding a second predetermined motive power, therebyoperating the refrigerating cycle.

The present invention also provides a device for controlling arefrigerating cycle as described above wherein when the control sectionperforms a predetermined processing and judges to select a channel bythe channel selector valve or to halt an operation of the refrigeratingcycle,

the control section sends output signals to the compressor drivingsection: to drive the power source of the compressor with a thirdpredetermined capacity so as to generate a motive power lower than asecond predetermined motive power; or to halt the operation of thecompressor, thereby halting the operation of the refrigerating cycle.

The present invention also provides a device for controlling arefrigerating cycle as described above wherein when the control sectionperforms a predetermined processing and judges to select a channel bythe channel selector valve or to halt an operation of the refrigeratingcycle,

the control section sends output signals to the compressor drivingsection to halt the operation of the compressor, then keeps therefrigerating cycle standby for a third predetermined period of time,then sends output signals to the compressor driving section to start theoperation of the compressor, then renews position data in a memory unitto a first or second position after a first predetermined period oftime, thereby halting the operation of the compressor again.

The present invention further provides a device for controlling arefrigerating cycle as described above wherein when positional datamemorized by a memory unit of the control section indicate a first orsecond position, the control section starts an operation of therefrigerating cycle so that a motive power exceeding a firstpredetermined motive power is generated as an internal motive power ofthe channel selector valve.

The present invention also provides a device for controlling a channelselector valve communicating with a refrigerating cycle, which devicecomprises:

a control section that receives input signals sent from an operationcommand section for commanding an operation state of the refrigeratingcycle and from a physical quantity detector section for detecting a-physical quantity generated by the refrigerating cycle,

wherein the control section sends output signals to a driving sectionthat drives a drive source of at least one of a plurality of functionalcomponents communicated to the refrigerating cycle so as to control saidfunctional component and to control the refrigerating cycle, and whenjudging not to select a channel by using the channel selector valve onthe basis of a command of the operation command section, the controlsection sends output signals to a driving section for driving a powersource of a compressor so as to start an operation of the compressor ofthe refrigerating cycle and starts an operation of the refrigerant cycleso as to generate a motive power lower than a first predetermined motivepower, thereby a channel selector valve is passively controlled.

The present invention further provides a device for controlling arefrigerating cycle as described above wherein the control sectionstarts an operation of the compressor with a second predeterminedcapacity.

The present invention also provides a device for controlling arefrigerating cycle which controls a channel selector valve communicatedto the refrigerating cycle, the device comprising:

a control section that receives input signals sent from an operationcommand section for commanding an operation state of the refrigeratingcycle and from a physical quantity detector section for detecting aphysical quantity generated by the refrigerating cycle,

wherein the control section sends output signals to a driving sectionthat drives a drive source of at least one of a plurality of functionalcomponents communicated to the refrigerating cycle so as to control saidfunctional component and to control the refrigerating cycle, and whenjudging not to select a channel by using the channel selector valve onthe basis of a command of the operation command section, the controlsection sends output signals to a driving section for driving a powersource of a compressor so as to start an operation of the compressor ofthe refrigerating cycle and starts an operation of the refrigerant cycleso as to generate a motive power exceeding a first predetermined motivepower, thereby the channel selector valve is passively controlled.

The present invention also provides a device for controlling arefrigerating cycle as described above wherein when the control sectionperforms a predetermined processing and judges to halt an operation ofthe refrigerating cycle,

the control section sends output signals to the compressor drivingsection so as to halt the operation of the compressor, then keeps therefrigerating cycle standby for a third predetermined period of timewithout renewing position data in a memory unit.

According to a channel selector valve of the present invention a channelselection of fluid by the channel selector valve is performed byemploying non-electric motive power generated when a control sectioncontrols a physical quantity of the fluid.

According to one embodiment of channel selector valve of the presentinvention a channel selection of fluid by the channel selector valve ispassively performed using motive power generated by anon-electrically-driven drive source provided separately from thechannel selector valve.

According to another channel selector valve of the present invention atleast one of element components in a refrigerating cycle having thechannel selector valve generates a motive power, by which a channelselection of fluid by the channel selector valve is passively performed.

According to another channel selector valve of the present invention achange in physical quantity generated in a refrigerating cycle due to anaction of at least one element component in the refrigerating cycleconstitutes at least a part of a motive power that is used for a channelselection of fluid by the channel selector valve.

According to a further embodiment of a channel selector valve of thepresent invention when at least one change among changes in pressure,differential pressure and flow rate of fluid in the channel selectorvalve arising from an action of an element component in therefrigerating cycle takes place, the change as a change in a physicalquantity arising in the refrigerating cycle is used for a selection of achannel by the channel selector valve.

According to a further embodiment of a channel selector valve of thepresent invention a selection of a place where a main port formed in thehousing is communicated to through the interior of the housing betweentwo selector ports is achieved by moving a movable member between thefirst and second positions by driving means that uses non-electricmotive power generated when a control section controls a physicalquantity of the fluid.

According to another embodiment of the channel selector valve of thepresent invention a motive power, which is used for selecting a channelof fluid by a channel selector valve, includes a change in a physicalquantity generated due to an action of at least one of elementcomponents in a refrigerating cycle, thereby a channel selection of thefluid is passively performed by using the motive power.

According to another embodiment of a channel selector valve of thepresent invention when at least one change among changes in pressure,differential pressure and flow rate of fluid in the channel selectorvalve, which is generated by an action of at least one element componentin the refrigerating cycle, takes place, the change as a change inphysical quantity generated in the refrigerating cycle is used for aselection of a channel by the channel selector valve.

According to another embodiment of a channel selector valve of thepresent invention the channel selector valve is constructed as afour-way selector valve.

According to a further embodiment of a channel selector valve of thepresent invention a first selector port of a first three-way selectorvalve is connected to a second selector port of a second three-wayselector valve, while a second selector port of the first three-wayselector valve is connected to a first selector port of the secondthree-way selector valve, a main port of the first three-way selectorvalve is an inlet port formed in the housing, through which fluidintroduced from the exterior to the interior of the housing of the firstthree-way selector valve passes, while a main port of the secondthree-way selector valve is an outlet port formed in the housing,through which the fluid discharged from the interior to the exterior ofthe housing of the second three-way selector valve passes, then, amovable member of the second three-way selector valve moves to a secondposition when the movable member of the first three-way selector valvemoves to the first position, while the movable member of the secondthree-way selector valve moves to a first position when the movablemember of the first three-way selector valve moves to the secondposition, thereby the channel selector valve is constituted as afour-way selector valve by the first and second three-way selectorvalves.

According to a further embodiment of a channel selector valve of thepresent invention when a difference between a pressure of fluid at afirst selector port and that at a second selector port cancels out, amovable member of a first three-way selector valve situated at a firstposition is moved to a second position by a first drive mechanism of thefirst three-way selector valve, while a movable member of the firstthree-way selector valve situated at the second position is moved to thefirst position by a second drive mechanism.

According to another embodiment of a channel selector valve of thepresent invention in a first three-way selector valve, when a fluidpressure at a main port exceeds a first predetermined value, a movablemember is situated at a first position by the fluid pressure, therebythe main port communicates with a first selector port and an energizingforce is stored in a first storing means for storing energizing force,while when a fluid pressure at the main port is lower than a firstpredetermined value, the movable member is moved from the first positionto a fourth position against the fluid pressure at the main port by theenergizing force stored in the first storing means for storingenergizing force, thereby a place where the main port is communicated tois switched from the first selector port to the second selector port.

Then, in a state that the movable member is situated at the fourthposition, when the fluid pressure at the main port exceeds a secondpredetermined value, the movable member is moved from the fourthposition to the second position by the fluid pressure and an energizingforce is stored in the second storing means for storing energizingforce, while when a fluid pressure at the main port is lower than thesecond predetermined value, the movable member is moved from the secondposition to a third position against the fluid pressure at the main portby the energizing force stored in the second storing means for storingenergizing force, thereby a place where the main port is communicated tois switched from the second selector port to the first selector port.

According to another embodiment of a channel selector valve of thepresent invention out of an inlet port formed in the housing, throughwhich fluid introduced from the exterior to the interior of the housingpasses, and an outlet port, through which the fluid discharged from theinterior to the exterior of the housing passes, the inlet port is set tobe a main port, then, when a movable member is situated at a firstposition, the inlet port and a first selector port are communicated witheach other inside the housing, while the outlet port and a secondselector port are communicated with each other inside the housing, onthe other hand, when the movable member is situated at a secondposition, the inlet port and the second selector port are communicatedwith each other inside the housing, while the outlet port and the firstselector port are communicated with each other inside the housing.

According to a further embodiment of a channel selector valve of thepresent invention a movable member is moved between first and secondpositions by changing a difference between a pressure of fluidintroduced from the exterior of the housing and a pressure of fluiddischarged to the exterior of the housing by using a motive powergenerated by a non-electrically-driven drive, thereby a linearslide-type four-way selector valve is constructed by a channel selectorvalve.

According to a further embodiment of a method of driving the channelselector valve of the present invention when there is no differencebetween a pressure of fluid in a first space and a pressure of fluid ina second pressure chamber, a movable member energized by an energizingmeans is situated at a first position, thereby a first selector port isset to be a place where the fluid, which is introduced from the exteriorof the housing to the first space by way of an inlet port, is dischargedto, while a second selector port is set to be a place where the fluid,which is discharged from a second space to the exterior of the housingby way of an outlet port, is introduced from.

When a pressure of the fluid, which is introduced from the exterior ofthe housing to the first space of the first pressure chamber by way ofthe inlet port, is raised so that a force, which exceeds a resultantforce of the energizing force by the energizing means and a force thatthe fluid in the second pressure chamber acts on the movable member, isacted on the movable member from the first pressure chamber side, themovable member situated at the first position by the energizing force bythe energizing means moves to a second position against the energizingforce by the energizing means, thereby the second selector port is setto be a place where the fluid, which is introduced from the exterior ofthe housing to the first space by way of the inlet port, is dischargedto, while the first selector port is set to be a place where the fluid,which is discharged from the second space to the exterior of the housingby way of the outlet port, is introduced from.

Then, when the movable member moves from the first position to thesecond position, since a pressure of the fluid in the second pressurechamber is compressed to become high, a pressure of the fluid, which isintroduced from the exterior of the housing into the first space of thefirst pressure chamber by way of the inlet port, is set high so that theforce, which exceeds a resultant force of the energizing force by theenergizing means and a force that the fluid in the second pressurechamber acts on the movable member, is acted on the movable member fromthe first pressure chamber side, thereby the movable member moved fromthe first position is held at the second position.

According to another embodiment of a channel selector valve of thepresent invention when a force acted on a movable member from a firstpressure chamber side by a pressure of the fluid, which is introducedinto a first space of the housing by way of a inlet port, is equal to orlower than a resultant force of the energizing force by the energizingmeans, a force that the fluid in a second pressure chamber acts on themovable member and a static friction force between a valve seat and themovable member, the movable member stays at a first position.

Therefore, a first selector port is set to be a place where the fluid,which is introduced from the exterior of the housing to the first spaceby way of the inlet port, is discharged to, while a second selector portis set to be a place where the fluid, which is discharged from a secondspace to the exterior of the housing by way of an outlet port, isintroduced from.

On the other hand, when a force acted on the movable member from thefirst pressure chamber side by a pressure of the fluid, which isintroduced into the first space of the housing by way of the inlet port,exceeds a resultant force of the energizing force by the energizingmeans, a force that the fluid in the second pressure chamber acts on themovable member and a static friction force between the valve seat andthe movable member, the movable member moves to the second positionagainst the energizing force by the energizing means.

Therefore, the second selector port is set to be a place where thefluid, which is introduced from the exterior of the housing to the firstspace by way of the inlet port, is discharged to, while the firstselector port is set to be a place where the fluid, which is dischargedfrom the second space to the exterior of the housing by way of theoutlet port, is introduced from.

Then, after the movable member moves to the second position, when aforce acted on the movable member from the first pressure chamber sideby a pressure of the fluid, which is introduced into the first space ofthe housing by way of the inlet port, exceeds a force, which is resultedby subtracting a static friction force between the valve seat and themovable member from a resultant force consisting of the energizing forceby the energizing means and a force that the fluid in the secondpressure chamber acts on the movable member, the movable member keepsstaying at the second position against the energizing force by theenergizing means.

According to a further embodiment of a method of driving the channelselector valve of the present invention when the channel selector valveis driven, if a movable member moves from a first position to a secondposition, the fluid in a second pressure chamber is compressed to give achange in pressure with respect to fluid in a first space, however,since the first space communicates with the second pressure chamberthrough an equalizing path, a pressure of fluid in the first spacebecomes close to that in the second pressure chamber.

Then, the force acted on the movable member by the fluid in the firstspace soon becomes equal to the resultant force consisting of theenergizing force by the energizing means and the force that the fluid inthe second pressure chamber acts on the movable member, then becomeseven lower than that, resulting in that the movable member is ready tomove toward the first position from the second position, however, thestatic friction force between the valve seat and the movable member actsagainst the energizing force by the energizing means even after adifference between the pressure of the fluid in the first space and thatin the second pressure chamber decreases, thereby the movable member isheld at the second position by the static friction force.

According to a further embodiment of a channel selector valve of thepresent invention when a physical quantity in the housing is changed bythe fluid, which is introduced from the exterior into the interior ofthe housing by way of an inlet port of the housing, the change inphysical quantity is utilized as at least a part of a motive power formoving a movable member between a first and second position, by thirdand fourth drive mechanisms.

According to a further embodiment of a channel selector valve of thepresent invention when a selector valve element of a pilot valve issituated at a fifth position, an outlet port communicates with a thirdpressure chamber through a second main port of the pilot valve and afourth pressure chamber, while when the selector valve element of thepilot valve is situated at a sixth position, the outlet portcommunicates with a second pressure chamber through a second main portof the pilot valve and the fifth pressure chamber.

Therefore, if a pressure of the fluid at an inlet port from which thefluid is introduced exceeds a pressure of the fluid at the outlet portfrom which the fluid is discharged, the selector valve element of thepilot valve is moved between the fifth and sixth position so that eitherthe second pressure chamber or the third pressure chamber, placedsandwiching the first pressure chamber with each other, is selected as achamber, a fluid pressure of which is lower than that in the first spaceof the first pressure chamber, thereby a direction of the movable memberto move by a difference in pressure of the fluid is selected between adirection from a first position to a second position and that from thesecond position to the first position.

According to a further embodiment of a channel selector valve of thepresent invention when a difference between a pressure of fluid in asecond pressure chamber and that in a third pressure chamber cancelsout, a selector valve element is moved from one to another between fifthand sixth positions by second driving means.

According to another embodiment of a channel selector valve of thepresent invention when a selector valve element of a pilot valve issituated at a seventh position, a second main port communicating with anoutlet port communicates with a fourth pressure chamber communicatingwith a third pressure chamber, thereby the outlet port communicates withthe third pressure chamber through the pilot valve.

In this state, when a pressure of the fluid in a first space of a firstpressure chamber communicating with an inlet port increases to exceed apressure of the fluid in the third pressure chamber communicating withthe outlet port, a movable member moves so that the volume of the thirdpressure chamber decreases, resulting in that the volume of a secondpressure chamber increases, in other words, the movable member movesfrom a second position to a first position, then the third pressurechamber is isolated from the fourth pressure chamber by a first subvalvewhile the second pressure chamber is communicated to a fifth pressurechamber by a second subvalve.

Then, a pressure of the fluid in the second pressure chambercommunicating with a first space by a first equalizing path increases inresponse to an increases in that in the first space, thereby when apressure of the fluid in the fifth pressure chamber communicating withthe second pressure chamber increases and exceeds a third predeterminedvalue, the selector valve element situated at the seventh position movesto a fifth position and an energizing force is stored in a third storingmeans for storing energizing force.

Thereafter, when a pressure of the fluid in the second or fifth pressurechamber becomes lower than a third predetermined value due to a decreasein a pressure of the fluid in the first space, the selector valveelement is moved from the fifth position to an eighth position against apressure of the fluid in the fifth pressure chamber by an energizingforce of the third storing means for storing energizing force, thereby asecond main port communicating with the outlet port communicates withthe fifth pressure chamber communicating with the second pressurechamber, resulting in that the outlet port communicates with the secondpressure chamber through the pilot valve.

In this state, when a pressure of the fluid in the first space of thefirst pressure chamber communicating with the inlet port increases toexceed a pressure of the fluid in the second pressure chambercommunicating with the outlet port, the movable member moves so that thevolume of the second pressure chamber decreases, resulting in that thevolume of the third pressure chamber increases, in other words, themovable member moves from a first position to a second position, thenthe third pressure chamber is communicated to the fourth pressurechamber by a first subvalve while the second pressure chamber isisolated from the fifth pressure chamber by a second subvalve.

Then, a pressure of the fluid in the third pressure chambercommunicating with the first space by a second equalizing path increasesin response to an increases in that in the first space, thereby when apressure of the fluid in the fourth pressure chamber communicating withthe third pressure chamber increases and exceeds a fourth predeterminedvalue, the selector valve element situated at the eighth position movesto a sixth position and an energizing force is stored in a fourthstoring means for storing energizing force.

Thereafter, when a pressure of the fluid in the third or fourth pressurechamber becomes lower than a fourth predetermined value due to adecrease in a pressure of the fluid in the first space, the selectorvalve element is moved from the sixth position to the seventh positionagainst a pressure of the fluid in the fourth pressure chamber by anenergizing force of the fourth storing means for storing energizingforce, thereby the second main port communicating with the outlet portcommunicates with the fourth pressure chamber communicating with thethird pressure chamber, resulting in that the outlet port communicateswith the third pressure chamber through the pilot valve.

Therefore, in this state, when a pressure of the fluid in the firstspace of the first pressure chamber communicating with the inlet portincreases to exceed a pressure of the fluid in the third pressurechamber communicating with the outlet port, the movable member movesfrom the second position to the first position.

According to a further embodiment of a channel selector valve of thepresent invention when a difference between a pressure of fluid in asecond pressure chamber and that in a third pressure chamber cancelsout, a selector valve element is moved from one to another between afifth and sixth positions by second driving means.

When the selector valve element of a pilot valve is situated at thefifth position, the inlet port communicates with a second pressurechamber through a third main port of the pilot valve and a fifthpressure chamber, while when the selector valve element of the pilotvalve is situated at a sixth position, the inlet port communicates withthe third pressure chamber through a third main port of the pilot valveand a fourth pressure chamber.

According to another embodiment of a channel selector valve of thepresent invention when a selector valve element of a pilot valve issituated at a seventh position, a third main port communicating with ainlet port communicates with a fifth pressure chamber communicating witha second pressure chamber, thereby the inlet port communicates with thesecond pressure chamber through the pilot valve.

In this state, when a pressure of the fluid in a first space of a firstpressure chamber communicating with the inlet port increases, a movablemember moves so that the volume of the second pressure chamberincreases, resulting in that the volume of a third pressure chamberdecreases, in other words, the movable member moves from a secondposition to a first position.

Then, a pressure of the fluid in the second pressure chambercommunicating with the first space by a first equalizing path increasesin response to an increases in that in the first space, thereby when apressure of the fluid in the fifth pressure chamber communicating withthe second pressure chamber increases and exceeds a third predeterminedvalue, the selector valve element situated at the seventh position movesto a fifth position and an energizing force is stored in a third storingmeans for storing energizing force.

Thereafter, when a pressure of the fluid in the second or fifth pressurechamber becomes lower than a third predetermined value due to a decreasein a pressure of the fluid in the first space, the selector valveelement is moved from the fifth position to an eighth position against apressure of the fluid in the fifth pressure chamber by an energizingforce of the third storing means for storing energizing force, thereby athird main port communicating with the inlet port communicates with afourth pressure chamber communicating with the third pressure chamber,resulting in that the inlet port communicates with the third pressurechamber through the pilot valve.

In this state, when a pressure of the fluid in the first space of thefirst pressure chamber communicating with the inlet port increases, themovable member moves so that the volume of the third pressure chamberincreases, resulting in that the volume of the second pressure chamberdecreases, in other words, the movable member moves from the firstposition to the second position.

Then, a pressure of the fluid in the third pressure chambercommunicating with the first space by a second equalizing path increasesin response to an increases in that in the first space, thereby when apressure of the fluid in the fourth pressure chamber communicating withthe third pressure chamber increases and exceeds a fourth predeterminedvalue, the selector valve element situated at the eighth position movesto the sixth position and an energizing force is stored in a fourthstoring means for storing energizing force.

Thereafter, when a pressure of the fluid in the third or fourth pressurechamber becomes lower than a fourth predetermined value due to adecrease in a pressure of the fluid in the first space, the selectorvalve element is moved from the sixth position to the seventh positionagainst a pressure of the fluid in the fourth pressure chamber by anenergizing force of the fourth storing means for storing energizingforce, thereby the third main port communicating with the inlet portcommunicates with the fifth pressure chamber communicating with thesecond pressure chamber, resulting in that the inlet port communicateswith the second pressure chamber through the pilot valve.

Therefore, in this state, when a pressure of the fluid in the firstspace of the first pressure chamber communicating with the inlet portincreases, the movable member moves from the second position to thefirst position.

According to another embodiment of a channel selector valve of thepresent invention when an internal pressure of the housing is changed bythe fluid, which is introduced from the exterior of the housing into theinterior thereof through an inlet port of the housing, one drivemechanism out of third and fourth drive mechanisms of the driving meansmoves a movable member between first and second positions by employing achange in physical quantity in the housing as at least a part of amotive power.

When the movable member is moved by the one drive mechanism, anenergizing force is stored in the energizing means received in thehousing, then another drive mechanism out of the third and fourth drivemechanisms moves the movable member between the first and secondpositions by employing the energizing force stored in the energizingmeans as at least a part of a motive power.

According to another embodiment of a channel selector valve of thepresent invention a latch mechanism selectively controls a movement of amovable member, which is moved by a driving means from one position toanother position between the first and second positions, thereby themovable member situated at either the first or second position is stayedat one position or moved to another position selectively.

According to another embodiment of a channel selector valve of thepresent invention a latch mechanism performs a first state, in which amovable member that is moved from one position to another positionbetween the first and second positions by a driving means is held at theone position, while the latch mechanism performs a second state, inwhich the movable member that is allowed to move from one position toanother position between the first and second positions moves from theone position to the another position.

According to a further embodiment of a channel selector valve of thepresent invention when a movement of a latch piece is controlled, amovement of a movable member, to which the latch piece follow, iscontrolled at one position.

According to a further embodiment of a method of driving the channelselector valve of the present invention before a movable member is movedfrom one position to another position by the driving means, the movablemember is once moved in a direction of moving from another position toone position, then a control of a movement of the movable member at theone position by a latch mechanism is removed, thereby allowing themovable member to move from the one position to the another position.

Moreover, when the movable member is moved from the one position towardthe another position after the movable member is moved from the anotherposition to the one position by the driving means, a movement of themovable member is controlled by the latch mechanism, thereby the movablemember is held at the one position.

According to another embodiment of a channel selector valve of thepresent invention when a third drive mechanism generates a motive powerin order to move a movable member of a channel selector valve from oneposition to another position between first and second positions, avalve-opening member is about to move from a valve-closing position to avalve-opening position by motive power, thereby this movement of thevalve-opening member is selectively controlled by a second latchmechanism.

Here, when the second latch mechanism controls a movement of thevalve-opening member, since the valve-opening member is held at avalve-closing position and does not move to the valve-opening position,the pilot valve is held in its closed state and an attenuation mechanismdoes not act, thereby a motive power generated by a fourth drivemechanism is not attenuated and a movement of the movable member fromthe another position to the one position between the first and secondpositions by the motive power generated by the fourth drive mechanism isprohibited.

To the contrary, when the second latch mechanism does not control amovement of the valve-opening member from the valve-closing position tothe valve-opening position, the valve-opening member moves from thevalve-closing position to the valve-opening position, the pilot valve isopened by this valve-opening member that has moved to the valve-openingposition, thereby the attenuation mechanism acts so as to attenuate themotive power generated by the fourth drive mechanism and a movement ofthe movable member from the another position to the one position betweenthe first and second positions by the motive power generated by thefourth drive mechanism is allowed.

According to another embodiment of a channel selector valve of thepresent invention if a second latch mechanism alternately repeats thirdand fourth states, when a movable member is moved from one position toanother position by a motive power generated by a third drive mechanism,a state that a movement of the movable member from the another positionto the one position by a motive power generated by a fourth drivemechanism is allowed and a state that a movement of the movable memberfrom the another position to the one position by a motive powergenerated by the fourth drive mechanism is prohibited are alternatelyproduced.

According to a further embodiment of a method of driving the channelselector valve of the present invention when a drive source of a thirddrive mechanism is allowed to generate a motive power again after thegeneration of a motive power by a drive source of the third drivemechanism is halted, a second latch mechanism is transferred between astate in which a movement of a valve-opening member from a valve-closingposition to a valve-opening position is controlled and a state in whichsaid control is removed, thereby the system can be transferred from onestate, in which a movable member can move from the another position tothe one position by using a motive power generated by a fourth drivemechanism, to another state in which the movable member cannot move fromthe another position to the one position, or the system can betransferred from the another state to the one state.

According to a further embodiment of a channel selector valve of thepresent invention if a movable member keeps staying at a first position,a place where the fluid, which is introduced from the exterior of thehousing into a first space by way of an inlet port, is discharged to afirst selector port, in addition, a place where the fluid, which isdischarged from a second space to the exterior of the housing by way ofan outlet port, is introduced from is still a second selector port,therefore a pressure of the fluid in a second pressure chambercommunicating with the first selector port by way of the communicationpipe becomes equal to a pressure of the fluid in the first spacecommunicating with the first selector port or that at the inlet port.

Therefore, as long as a force applied to a movable member from the firstpressure chamber side due to a pressure of the fluid introduced into thefirst space of the housing by way of the inlet port is lower than aresultant force of the energizing force by the energizing means and aforce that the fluid in the second pressure chamber acts on the movablemember, or is lower than a force consisting of said resultant force anda static friction force between the seat valve and the movable member,the movable member keeps staying at a first position, consequently, aplace, to which the inlet port or the outlet port is communicated, isnot selected (i.e. not changed).

To the contrary, when a force applied to the movable member from thefirst pressure chamber side due to a pressure of the fluid introducedinto the first space of the housing by way of the inlet port exceeds aresultant force of the energizing force by the energizing means and aforce that the fluid in the second pressure chamber acts on the movablemember, or exceeds a force consisting of said resultant force and astatic friction force between the seat valve and the movable member, themovable member moves from the first position to a second position,thereby a place where the fluid, which is introduced from the exteriorof the housing into the first space by way of the inlet port, isdischarged to is selected to be the second selector port, in addition, aplace where the fluid, which is discharged from the second space to theexterior of the housing by way of the outlet port, is introduced from isselected to be the first selector port.

Therefore, a pressure of the fluid in the second pressure chambercommunicating with the first selector port by way of the communicationpipe becomes equal to a pressure of the fluid at the outlet portcommunicating with the first selector port, then said pressure becomesdifferent from a pressure of the fluid at the inlet port communicatingwith the first space.

Consequently, as long as a pressure of the fluid at the inlet port isthereafter kept so that a force applied to the movable member from thefirst pressure chamber side due to a difference between a pressure ofthe fluid at the outlet port and that at the inlet port exceeds aresultant force consisting of the energizing force by the energizingmeans and a force that the fluid in the second pressure chamber acts onthe movable member, or exceeds a force, which is resulted by subtractinga static friction force between the valve seat and the movable memberfrom said resultant force consisting of the energizing force by theenergizing means and a force that the fluid in the second pressurechamber acts on the movable member, the movable member keeps staying atthe second position against an energizing force by the energizing means,thereby a place to which the inlet port or the outlet port iscommunicated is kept as selected (i.e. as changed).

Then, after the movable member has moved to the second position, when apressure of the fluid at the inlet port decreases so that a forceapplied to the movable member from the first pressure chamber side dueto a difference between a pressure of the fluid at the outlet port andthat at the inlet port is lower than a resultant force consisting of theenergizing force by the energizing means and a force that the fluid inthe second pressure chamber acts on the movable member, or is lower thana force, which is resulted by subtracting a static friction forcebetween the valve seat and the movable member from said resultant forceconsisting of the energizing force by the energizing means and a forcethat the fluid in the second pressure chamber acts on the movablemember, the movable member moves from the second position to the firstposition by an energizing force of the energizing means.

Thereby, a place where the fluid, which is introduced from the exteriorof the housing into the first space by way of the inlet port, isdischarged to is selected to be a first selector port, in addition, aplace where the fluid, which is discharged from a second space to theexterior of the housing by way of the outlet port, is introduced from isselected to be the second selector port.

According to a further embodiment of a channel selector valve of thepresent invention if a movable member is moved from a first position toa second position so that a channel of the fluid is selected by thechannel selector valve using a motive power generated by anon-electrically-driven drive source, the movable member is held at thesecond position by a state-holding mechanism.

According to another embodiment of a channel selector valve of thepresent invention when a movable member is situated at a first position,an energizing of a second selector valve element by energizing means forenergizing the selector valve is allowed, thereby a state-holdingselector valve is set in a first state in which a second pressurechamber is communicated to the exterior of the housing through a firstintroducing port, while when the movable member is situated at thesecond position, against the energizing by the energizing means forenergizing the selector valve, the state-holding selector valve is setin a second state in which the second pressure chamber is communicatedto the exterior of the housing through a second introducing port.

Whether the movable member is situated at the first position or a secondposition depends upon whether a force applied to the movable member froma first space side is higher or not than a force applied to the movablemember from the second pressure chamber side, as a result of taking thefollowing forces into consideration, said following forces are a forceapplied to the movable member by the fluid in the first space, a forceapplied to the movable member by the fluid flowed into the secondpressure chamber, a static friction force between a valve seat and themovable member, and an energizing force by the energizing means.

Therefore, when the movable member is situated at the first position, aslong as a pressure of the fluid at an inlet port communicating with thefirst space is set so that a force applied to the movable member fromthe second pressure chamber side, which depends on a pressure of thefluid at a place to which the first introducing port communicating withthe second pressure chamber is communicated, exceeds a force applied tothe movable member from the first space side, the movable member keepsstaying at the first position, thereby a first selector port out of twoselector ports formed in the housing communicates with the inlet portthrough the first space, while a second selector port out of the twoselector ports communicates with an outlet port through a second space.

On the other hand, when a pressure of the fluid in the first spaceincreases so that a force applied to the movable member from the firstspace side exceeds a force applied to the movable member from the secondpressure chamber side, which depends on a pressure of the fluid at aplace to which a first introducing port communicating with the secondpressure chamber is communicated, the movable member moves from thefirst position to the second position in the housing, thereby the firstselector port out of the two selector ports formed in the housingcommunicates with the outlet port through the first space, while thesecond selector port out of the two selector ports communicates with theinlet port through the second space, and a place to which the secondpressure chamber is communicated is selected from the first introducingport to the second introducing port.

Here, if a pressure of the fluid in a place to which the secondintroducing port is communicated is set lower to some extent than thatin a place to which the first introducing port is communicated, evenwhen a pressure of the fluid in the first space decreases to someextent, a force applied to the movable member from the first space sideexceeds a force applied to the movable member from the second pressurechamber side, thereby the movable member keeps staying at the secondposition.

However, when a pressure of the fluid in the first space markedlydecreases so that a force applied to the movable member from the secondpressure chamber side exceeds a force applied to the movable member fromthe first space side, the movable member moves from the second positionto the first position in the housing, thereby the first selector portout of the two selector ports formed in the housing communicates withthe inlet port through the first space, while the second selector portout of the two selector ports communicates with the outlet port throughthe second space, and a place to which the second pressure chamber iscommunicated is selected from the second introducing port to the firstintroducing port.

Since a pressure of the fluid in a place to which the first introducingport is communicated is set higher to some extent than that in a placeto which the second introducing port is communicated, even when apressure of the fluid in the first space is kept very low after themovable member has moved from the second position to the first position,a force applied to the movable member from the second pressure chamberside exceeds a force applied to the movable member from the first spaceside, thereby the movable member keeps staying at the first position.

According to a further embodiment of a channel selector valve of thepresent invention when a movable member is situated at a first position,as long as a force applied to the movable member by the fluid in a firstspace is lower than a resultant force of energizing force by anenergizing means and a force applied to the movable member by the fluid,which flowed into a second pressure chamber from a place to which afirst introducing port is communicated, or is lower than a forceconsisting of said resultant force and a static friction force between aseat valve and the movable member, the movable member keeps staying atthe first position.

On the other hand, a pressure of the fluid in the first space increasesso that a force applied to the movable member by the fluid in the firstspace exceeds a resultant force of the energizing force by theenergizing means and a force applied to the movable member by the fluid,which flowed into the second pressure chamber from a place to which thefirst introducing port is communicated, or exceeds a force consisting ofsaid resultant force and a static friction force between the seat valveand the movable member, the movable member moves from the first positionto a second position in the housing.

Here, if a pressure of the fluid in a place to which a secondintroducing port is communicated is set lower to some extent than thatin a place to which the first introducing port is communicated, evenwhen a pressure of the fluid in the first space decreases to someextent, a force applied to the movable member from the first space sideexceeds a resultant force consisting of the energizing force by theenergizing means and a force applied to the movable member by the fluidflowed into the second pressure chamber, or exceeds a force, which isresulted by subtracting a static friction force between the valve seatand the movable member from said resultant force consisting of theenergizing force by the energizing means and a force applied to themovable member by the fluid flowed into the second pressure chamber,thereby the movable member keeps staying at the second position.

Since a pressure of the fluid in a place to which the first introducingport is communicated is set higher to some extent than that in a placeto which the second introducing port is communicated, even when apressure of the fluid in the first space is kept very low after themovable member has moved from the second position to the first position,a resultant force consisting of the energizing force by the energizingmeans and a force applied to the movable member by the fluid flowed intothe second pressure chamber, or a force, which is resulted bysubtracting a static friction force between the valve seat and themovable member from said resultant force consisting of the energizingforce by the energizing means and a force applied to the movable memberby the fluid flowed into the second pressure chamber, exceeds a forceapplied to the movable member from the first space side, thereby themovable member keeps staying at the first position.

According to another embodiment of a method of driving the channelselector valve of the present invention when the channel selector valveis driven, a pressure of fluid introduced into a first space from theexterior of the housing by way of an inlet port is set higher than apredetermined value, so that a force, which is applied to a movablemember by fluid existing in a first space in a direction from a firstposition to a second position, is set stronger than a force, which isapplied to the movable member by fluid existing in a place to which asecond pressure chamber is communicated in a direction from the secondposition to the first position, thereby the movable member moves fromthe first position to the second position, in addition thereafter, apressure of fluid existing in the first space and a pressure of fluidexisting in the second pressure chamber are set so that the movablemember is kept staying at the second position.

According to another embodiment of a channel selector valve of thepresent invention an opening ratio of an electrically-driven expansionvalve in a refrigerating cycle is changed to change a pressure of fluidin the refrigerating cycle, thereby a balance, between a force that thefluid in the channel selector valve is applied to a movable member tomove from a first position to a second position and a force that thefluid in the channel selector valve is applied to the movable member tomove from the second position to the first position, changes, therebythe movable member moves between the first and second positions.

According to another embodiment of a channel selector valve of thepresent invention when a frequency of an oscillation generated by acompressor in a refrigerating cycle is changed, a member that respondsonly to a specific frequency produces a change in condition, then apressure of the fluid in a second pressure chamber changes, thereby abalance, between a force that the fluid in the channel selector valve isapplied to a movable member to move from a first position to a secondposition and a force that the fluid in the channel selector valve isapplied to the movable member to move from the second position to thefirst position, changes, thereby the movable member moves between thefirst and second positions.

According to a further embodiment of a channel selector valve of thepresent invention a heat-exchange capacity by a heat exchanger in arefrigerating cycle is adjusted and a difference in fluid pressure ischanged by a difference in amount of heat exchange by the heatexchanger, then a pressure of the fluid in the refrigerating cyclechanges, thereby a balance, between a force that the fluid in thechannel selector valve is applied to a movable member to move from afirst position to a second position and a force that the fluid in thechannel selector valve is applied to the movable member to move from thesecond position to the first position, changes, thereby the movablemember moves between the first and second positions.

According to a further embodiment of a channel selector valve of thepresent invention a rotary-type four-way selector valve is constructedby the channel selector valve, in which when a main valve element as amovable member rotates around the central axis in the housing so as tomove between a first and second positions, a place to which an inletport as a main port is communicated by communication means provided inthe main valve element is selected between a first selector port and asecond selector port out of two selector ports provided at an end sideof the housing.

According to another embodiment of a channel selector valve of thepresent invention one port formed on a valve seat out of an inlet portand an outlet port communicates with a first selector port of a valveseat when a main valve element is situated at a first position, whilecommunicates with a second selector port of the valve seat when the mainvalve element is situated at a second position, not by communicationmeans but by second communication means formed at one end surface of themain valve element that sits down on the valve seat.

According to another embodiment of a channel selector valve of thepresent invention by a communication channel for communicating one endsurface side of a main valve element to another end surface sidethereof, when the main valve element is situated at a first position, asecond selector port formed on a valve seat at one end side of thehousing communicates with another port formed at another end side of thehousing, while when the main valve element is situated at a secondposition, the second selector port formed on the valve seat at one endside of the housing communicates with a first selector port formed onthe valve seat.

According to another embodiment of a channel selector valve of thepresent invention when a main valve element is moved in a direction ofthe central axis of the housing by a driving means, this movement istransformed into a rotation around the central axis of the housing byconversion means of moving direction, thereby the main valve element isrotated between first and second positions.

According to a further embodiment of a channel selector valve of thepresent invention while a main valve element moves in a direction of thecentral axis of the housing, in the inside of a cam groove provided inone out of the main valve element and the housing, a cam follower pinprovided in another out of the main valve element and the housing moves,thereby a movement of the main valve element in a direction of thecentral axis of the housing is transformed into a rotation around thecentral axis of the housing.

Then, the cam groove has a first and second cam grooves continuing witheach other in the rotational direction of the main valve element, sincethe first cam groove is formed inclined so as to part from a valve seatin a direction of the central axis as being displaced in the rotationaldirection, while the second cam groove is formed inclined so as to movenearer to the valve seat in a direction of the central axis as beingdisplaced in the rotational direction, when the main valve elementproceeds and returns in a direction of the central axis of the housing,the main valve element rotates between the first and second positions,with the cam follower pin being guided along the first and second camgrooves.

According to another embodiment of a channel selector valve of thepresent invention a cam follower pin formed on a main valve element isdisposed between a first and second half of an inner housing, then eachend of the first and second half is joined together, thereby the mainvalve element is received in the inner housing and by the inner housingthe main valve element is movable in a direction of the central axis ofthe housing and is supported rotatably around the central axis.

According to a further embodiment of a channel selector valve of thepresent invention when a main valve element, which is moved in adirection of the central axis by a driving means, rotates around thecentral axis of the housing with its movement being transformed byconversion means of moving direction, one end surface of the main valveelement sits down on a valve seat only when situating at a first or asecond position, thereby one port of the valve seat selectivelycommunicates with one out of a first selector port and a second selectorport of the valve seat, by second communication means formed at one endsurface of the main valve element.

According to a further embodiment of a channel selector valve of thepresent invention when a main valve element is situated at a first orsecond position where one end surface of the main valve element sitsdown on a valve seat, a communication channel is opened by a subvalveopened by a valve-opening means, then one end surface side of the mainvalve element communicates with another end surface side thereof, and bythis communication channel another port, which is formed at another endside of the housing and forms a main port, communicates with a secondselector port formed on the valve seat when the main valve element issituated at the first position, while communicates with a first selectorport formed on the valve seat when the main valve element is situated atthe second position.

According to another embodiment of a channel selector valve of thepresent invention when a main valve element sat down on a valve seat ismoved in a direction away from the valve seat by a driving means, an ownweight of the main valve is utilized as at least a part of non-electricmotive power.

According to a further embodiment of a channel selector valve of thepresent invention when a main valve element sat down on a valve seat ismoved in a direction away from the valve seat by a driving means, anenergizing force stored in the energizing means for energizing the mainvalve element is utilized as at least a part of non-electric motivepower.

According to a further embodiment of a channel selector valve of thepresent invention when a main valve element away from a valve seat ismoved in a direction nearer to the valve seat by a driving means, anenergizing force stored in the second energizing means for energizingthe main valve element is utilized as at least a part of non-electricmotive power.

According to another embodiment of a channel selector valve of thepresent invention when a pressure of the fluid at one port exceeds thatat another port, a main valve element, situated at an intermediateposition by a resultant force of an energizing force of an energizingmeans for energizing the main valve element and that of a secondenergizing means for energizing the main valve element, moves in thedirection away from a valve seat with rotating against an energizingforce of a second energizing means for energizing the main valveelement.

To the contrary, when a pressure of the fluid at one port is lower thanthat at another port, the main valve element situated at a neutralposition, one end surface of which is away from the valve seat, moves inthe direction nearer to the valve seat with rotating against theenergizing force of the energizing means for energizing the main valveelement.

According to another embodiment of a channel selector valve of thepresent invention whether a cam follower pin, situated at anintermediate position of the cam groove, is in a first cam groove or ina second cam groove, when a pressure of the fluid at one port is lowerthan that at another port, a main valve element situated at the neutralposition moves in a direction nearer to the valve seat, then the camfollower pin moves to the groove by way of either one end of the firstcam groove or that of the second cam groove, thereby the main valveelement rotates to be situated at either a first or second position.

Then, in a state that the cam follower pin is situated in the groove,when a state that a pressure of the fluid at the one port is lower thanthat at the another port is canceled, the cam follower pin situated inthe groove moves to another end side of the cam groove by way of one endof the cam groove out of the first and second cam grooves, which issituated at a down stream side in the direction of the rotation, therebythe main valve element rotates around the central axis from the first orsecond position and the main valve element moves away from the valveseat to be situated at the neutral position.

According to another embodiment of a channel selector valve of thepresent invention whether a cam follower pin, situated at anintermediate position of a cam groove, is in a first cam groove or in asecond cam groove, when a pressure of the fluid at one port is higherthan that at another port, a main valve element situated at the neutralposition moves in the direction away from a valve seat, then the camfollower pin moves to the second groove by way of either another end ofthe first cam groove or that of the second cam groove, thereby the mainvalve element rotates to be situated at an intermediate position betweenthe first and second positions around the central axis.

Then, in a state that the cam follower pin is situated in the secondgroove, when a state that a pressure of the fluid at the one port ishigher than that at the another port is canceled, the cam follower pinsituated in the second groove moves to another end side of the camgroove by way of one end of the cam groove out of the first and secondcam grooves, which is situated at a down stream side in the direction ofthe rotation, thereby the main valve element rotates around the centralaxis from the intermediate position between the first and secondpositions and the main valve element moves nearer to the valve seat tobe situated at the neutral position.

According to a further embodiment of a channel selector valve of thepresent invention when a main valve element moves in a direction of thecentral axis or rotates around the central axis with respect to thehousing, a sliding resistance between the housing and the main valveelement is reduced by slide means.

According to another embodiment of a compressor with the channelselector valve of the present invention a compressor housing part, inwhich a high pressure chamber from which a fluid compressed by acompressing section of the compressor is introduced is formed, isintegrally formed with a housing part, in which an inlet port isprovided, out of the housing of the channel selector valve thereby thecompressor housing is integrated with the housing of the channelselector valve.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention a channel selector valve iscontrolled by controlling the functional components for controlling theoperation of a refrigerating cycle.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention a functional component iscontrolled to control an operation of a refrigerating cycle, therebygenerating a non-electrical motive power, by which a channel selectorvalve is passively controlled.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention a microcomputer, whichcontrols an operation of a refrigerating cycle, a functional componentis controlled to control an operation of the refrigerating cycle,thereby generating a non-electrical motive power, by which a channelselector valve is passively controlled.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention a functional component iscontrolled to control an operation of a refrigerating cycle, thereby aphysical quantity or a rate of change in a physical quantity isgenerated as a non-electrical motive power, by which a channel selectorvalve is passively controlled.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention a microcomputer, controlsan operation of a refrigerating cycle, a functional component iscontrolled to control an operation of the refrigerating cycle, thereby aphysical quantity or a rate of change in the physical quantity isgenerated as a non-electrical motive power, by which a channel selectorvalve is passively controlled.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention in order to generate anon-electrical motive power for controlling a channel selector valve, afunctional component is controlled on the basis of a physical quantity,which concerns with a control of an operation of a refrigerating cycle,selected from the group consisting of a pressure, temperature, rate offlow, voltage, current, electrical frequency and mechanical oscillationfrequency.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention the physical quantity,which is a non-electrical motive power and is generated by arefrigerating cycle, is a pressure, differential pressure or rate offlow with respect to fluid existing in a channel selector valve, and arate of change in a physical quantity, which is the non-electricalmotive power and is generated by the refrigerating cycle, is a rate ofchange in pressure, rate of change in differential pressure or rate ofchange in rate of flow with respect to the fluid.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention an operational condition ofa refrigerating cycle is commanded from an operation command section anda physical quantity generated by the refrigerating cycle is detected ina physical quantity detector section, then a control section receivesinput signals sent from an operation command section and a physicalquantity detector section. Then, the control section sends outputsignals to a driving section that drives a drive source of at least oneof a plurality of functional components communicated to therefrigerating cycle so as to control said functional component, and thedevice generates a non-electrical motive power by controlling therefrigerating cycle and passively controls the channel selector valve bysaid motive power.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention a control section controlsat least one of a plurality of functional components communicated to arefrigerating cycle so as to start an operation of the refrigeratingcycle, thereby controlling the channel selector valve in a statecorresponding to the start of an operation, which is commanded by theoperation command section.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention a control section starts tooperate a compressor communicated to a refrigerating cycle in adirection of inverse rotation when the control section decides to selecta channel selector valve on the basis of a command of an operationcommand section, thereby a channel is selected by the channel selectorvalve.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention a control section controlsat least one of a plurality of functional components communicated to arefrigerating cycle so as to operate the refrigerating cycle, therebycontrolling a channel selector valve in a state corresponding to theoperation, which is commanded by the operation command section.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention a control section controlsat least one of a plurality of functional components communicated to arefrigerating cycle so as to halt an operation of the refrigeratingcycle, thereby controlling a channel selector valve in a statecorresponding to the halt of the operation, which is commanded by theoperation command section.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention a channel selector valve isconstructed in a manner that a movable member moves so as to select achannel, and a control section comprises at least one unit selected fromthe group consisting of: a memory unit for memorizing position data of amovable member of a channel selector valve; a comparison unit and ajudge unit for comparing and judging, respectively, position data andoperation command data; and a learning unit learning on the basis ofphysical quantity data by a control of functional components and controldata of the channel selector valve.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention a control section receivesthe input signals, performs a predetermined processing and judgeswhether a channel is to be changed or not to be changed by a channelselector valve, then confirms a position on the basis of presentposition data, then sends a output signals to a driving section so as tocontrol the functional components in a refrigerating cycle, thenreceives new input signals after a predetermined period of time,confirms a position of a movable member, and sets position data of saidposition as new present position data when said position is changed to anew position.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention a control section confirmsa position of a movable member by at least one temperature detectionmeans, at least one pressure detection means, at least one magneticdetection means, at least one current detection means or a combinationthereof after a predetermined period of time, and then installs positiondata corresponding to said position into a memory unit of a controlsection.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention a microcomputer thatcontrols a refrigerating cycle is used, thereby controlling at least oneof a plurality of functional components communicated to therefrigerating cycle so as to control the refrigerating cycle, and inorder to control a driving section for driving a functional component sothat the position of a movable member is to be moved or not to be moved,the microcomputer performs a processing consisting of the steps of:

receiving input signals; confirming a position by taking out presentposition data of a movable member installed in a memory unit; carryingout an operation to decide whether the movable member is to be moved ofnot to be moved, comparing, and judging; selecting and deciding adriving section; outputting drive signals to the driving sectionselected and decided; judging a position of the movable member by inputsignals after a predetermined period of time, with or without moving aposition of the movable member by a physical quantity generated by atleast one functional component that is selected and decided in said stepof selecting and deciding or a rate of the physical quantity; andinstalling position data of a position of the movable member into thememory unit when said position is changed to a new position.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention an operational condition ofa refrigerating cycle is commanded from an operation command section anda physical quantity generated by the refrigerating cycle is detected ina physical quantity detector section, then a control section receivesinput signals sent from a operation command section and a physicalquantity detector section. Then, the control section sends outputsignals to a driving section that drives a drive source of at least oneof a plurality of functional components communicated to therefrigerating cycle so as to control said functional component forcontrolling an operation of the refrigerating cycle, and when judging toselect a channel by using the channel selector valve on the basis of acommand of the operation command section, the control section sendsoutput signals to a driving section for driving a power source of acompressor so as to start an operation of the compressor of therefrigerating cycle and starts an operation of the refrigerant cycle soas to generate a motive power exceeding a first predetermined motivepower, thereby the channel selector valve is passively controlled.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention an operational condition ofa refrigerating cycle is commanded from an operation command section anda physical quantity generated by the refrigerating cycle is detected ina physical quantity detector section, then a control section receivesinput signals sent from a operation command section and a physicalquantity detector section. Then, the control section sends outputsignals to a driving section that drives a drive source of at least oneof a plurality of functional components communicated to therefrigerating cycle so as to control said functional component forcontrolling an operation of the refrigerating cycle, and when judging toselect a channel by using a channel selector valve on the basis of acommand of the operation command section, the control section sendsoutput signals to a driving section for driving a power source of acompressor so as to start an operation of the compressor in a directionof inverse rotation and starts an operation of the refrigerant cycle soas to generate a motive power exceeding a third predetermined motivepower, thereby the channel selector valve is passively controlled.

According to another embodiment of the device for controlling arefrigerating cycle of the present invention a channel selector valveselects a channel by moving a movable member between first and secondpositions in response to an internal motive power, a control sectionmemorizes position data corresponding to the first or second position ofthe movable member in a memory unit thereof, the control section startsan operation of a refrigerating cycle when the position data indicatesthe second or first position, halts the operation of the refrigeratingcycle with renewing position data in the memory unit to the first orsecond position, respectively, after a first predetermined period oftime, and keeps the operation of the refrigerating cycle standby duringa third predetermined period of time.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention a control section operatesa compressor in a specific frequency immediately after startingoperation of the compressor and starts an operation of a refrigeratingcycle so that a motive power exceeding a first predetermined motivepower is generated as an internal motive power of the channel selectorvalve.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention a control section starts anoperation of a compressor with a first predetermined capacity.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention a control section starts anoperation of a compressor with a second predetermined capacity so that amotive power lower than a first predetermined motive power is generatedas an internal motive power of a channel selector valve, then operatesthe refrigerating cycle for a fourth predetermined period of time, thenhalts the operation of the refrigerating cycle for a fifth predeterminedperiod of time, and then starts an operation of the compressor with afirst predetermined capacity so that a motive power exceeding a firstpredetermined motive power is generated as an internal motive power ofthe channel selector valve.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention a control section sendsoutput signals to a throttle device driving section so that an openingratio of a throttle device of a refrigerating cycle is almost fullyopened or almost fully closed.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention a control section sendsoutput signals to a heat exchanger motor driving section so that a heatexchanger motor of a refrigerating cycle is kept halted.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention once a control sectionstarts an operation of a compressor, the control section sends outputsignals to a compressor driving section after a first predeterminedperiod of time and drives a power source of the compressor so that amotive power exceeding a second predetermined motive power is generated,thereby operating the refrigerating cycle.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention once a control sectionstarts an operation of a compressor, the control section sends outputsignals to a throttle device driving section so as to set the openingratio of the throttle device a predetermined opening ratio after a firstpredetermined period of time.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention once a control sectionstarts an operation of a compressor, the control section sends outputsignals to a heat exchanger motor driving section after a secondpredetermined period of time so as to start an operation of a heatexchanger motor, sends output signals to a compressor driving section soas to generate a motive power lower than a first predetermined motivepower, and drives a power source of a compressor so as to generate amotive power exceeding a second predetermined motive power, therebyoperating the refrigerating cycle.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention when a control sectionperforms a predetermined processing and judges to select a channel by achannel selector valve or to halt an operation of a refrigerating cycle,the control section sends output signals to a compressor drivingsection: to drive a power source of a compressor with a thirdpredetermined capacity so as to generate a motive power lower than asecond predetermined motive power; or to halt the operation of thecompressor, thereby halting the operation of the refrigerating cycle.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention when a control sectionperforms a predetermined processing and judges to select a channel by achannel selector valve or to halt an operation of a refrigerating cycle,the control section sends output signals to a compressor driving sectionto halt the operation of a compressor, then keeps the refrigeratingcycle standby for a third predetermined period of time, then sendsoutput signals to the compressor driving section to start the operationof the compressor, then renews position data in a memory unit to a firstor second position after a first predetermined period of time, therebyhalting the operation of the compressor again.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention when positional datamemorized by a memory unit of a control section indicate a first orsecond position, the control section starts an operation of arefrigerating cycle so that a motive power exceeding a firstpredetermined motive power is generated as an internal motive power of achannel selector valve.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention an operational condition ofa refrigerating cycle is commanded from an operation command section anda physical quantity generated by the refrigerating cycle is detected ina physical quantity detector section, then a control section receivesinput signals sent from an operation command section and a physicalquantity detector section. Then, the control section sends outputsignals to a driving section that drives a drive source of at least oneof a plurality of functional components communicated to therefrigerating cycle so as to control said functional component forcontrolling an operation of the refrigerating cycle, and when judgingnot to select (i.e. not to switch) a channel by using a channel selectorvalve on the basis of a command of the operation command section, thecontrol section sends output signals to a driving section for driving apower source of a compressor so as to start an operation of thecompressor of the refrigerating cycle and starts an operation of therefrigerant cycle so as to generate a motive power lower than a firstpredetermined motive power, thereby the channel selector valve ispassively controlled.

According to a further embodiment of a device for controlling arefrigerating cycle of the present invention a control section starts anoperation of a compressor with a second predetermined capacity.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention an operational condition ofa refrigerating cycle is commanded from an operation command section anda physical quantity generated by the refrigerating cycle is detected ina physical quantity detector section, then a control section receivesinput signals sent from an operation command section and a physicalquantity detector section. Then, the control section sends outputsignals to a driving section that drives a drive source of at least oneof a plurality of functional components communicated to therefrigerating cycle so as to control said functional component forcontrolling an operation of the refrigerating cycle, and when judgingnot to select (i.e. not to switch) a channel by using a channel selectorvalve on the basis of a command of the operation command section, thecontrol section sends output signals to a driving section for driving apower source of a compressor so as to start an operation of thecompressor of the refrigerating cycle and starts an operation of therefrigerant cycle so as to generate a motive power exceeding a firstpredetermined motive power, thereby the channel selector valve ispassively controlled.

According to another embodiment of a device for controlling arefrigerating cycle of the present invention when a control sectionperforms a predetermined processing and judges to halt an operation of arefrigerating cycle, the control section sends output signals to acompressor driving section so as to halt the operation of a compressor,then keeps the refrigerating cycle standby for a third predeterminedperiod of time without renewing position data in a memory unit.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to afirst embodiment of the present invention.

FIG. 2 is a view illustrating a schematic constitution of arefrigerating cycle, in which a sectional view of the channel selectorvalve of FIG. 1 in a cooling mode is shown.

FIG. 3 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to asecond embodiment of the present invention.

FIG. 4 is a front view illustrating a modified example of a channelselector valve according to the first or second embodiment of thepresent invention.

FIG. 5 is a side view of the channel selector valve of FIG. 4.

FIG. 6 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to athird embodiment of the present invention.

FIG. 7 is a view illustrating a schematic constitution of arefrigerating cycle, in which a sectional view of the channel selectorvalve of FIG. 6 in a cooling mode is shown.

FIG. 8 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to afourth embodiment of the present invention.

FIG. 9 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to afifth embodiment of the present invention.

FIG. 10 is a view illustrating a schematic constitution of arefrigerating cycle, in which a sectional view of the channel selectorvalve of FIG. 9 in a cooling mode is shown.

FIG. 11 is an enlarged sectional view of a primary part of a latchmechanism of FIG. 9.

FIG. 12 is an enlarged development of a primary part of an innercylinder of FIG. 11.

FIG. 13 is an enlarged sectional view of a primary part of a latchmechanism of FIG. 9.

FIG. 14 is an enlarged sectional view of a primary part of a latchmechanism of FIG. 9.

FIG. 15 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to asixth embodiment of the present invention.

FIG. 16 is a view illustrating a schematic constitution of a latchmechanism usable instead of the latch mechanism of FIG. 9 or 15.

FIG. 17 is a development of a cam groove, along which a cam follower pinof FIG. 16 moves.

FIG. 18 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to aseventh embodiment of the present invention.

FIG. 19 is an enlarged sectional view of a primary part of a pilot valvemechanism of FIG. 18.

FIG. 20 is an enlarged sectional view of a primary part of a pilot valvemechanism of FIG. 18.

FIG. 21 is an enlarged sectional view of a primary part of a pilot valvemechanism of FIG. 18.

FIG. 22 is a view illustrating a schematic constitution of arefrigerating cycle, in which a sectional view of the channel selectorvalve of FIG. 18 in a cooling mode is shown.

FIG. 23 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to aeighth embodiment of the present invention.

FIG. 24 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to aninth embodiment of the present invention.

FIG. 25 is a view illustrating a schematic constitution of arefrigerating cycle, in which a sectional view of the channel selectorvalve of FIG. 24 in a cooling mode is shown.

FIG. 26 is an enlarged sectional view of a primary part of astate-holding selector valve of FIG. 24.

FIG. 27 is an enlarged sectional view of a primary part of astate-holding selector valve of FIG. 24.

FIG. 28 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to atenth embodiment of the present invention.

FIG. 29 is an enlarged sectional view of a pilot oscillating valve ofFIG. 28.

FIG. 30 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to aeleventh embodiment of the present invention.

FIG. 31 is an enlarged sectional view of a differential pressureselector valve of FIG. 30.

FIG. 32 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to atwelveth embodiment of the present invention.

FIG. 33 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to athirteenth embodiment of the present invention.

FIG. 34 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to afourteenth embodiment of the present invention.

FIG. 35 is a view illustrating a schematic constitution of arefrigerating cycle employing a rotary channel selector valve, to whicha channel selector valve of the present invention can be applied.

FIG. 36 is a sectional view of a channel selector valve according to afifteenth embodiment of the present invention, which can be employed asthe rotary channel selector valve of FIG. 35.

FIG. 37 is a side view of an upper inner housing of FIG. 36.

FIG. 38 is a side view of a lower inner housing of FIG. 36.

FIG. 39 is a side view of each upper and lower inner housing of FIG. 36in a state of each of them being inserted in the outer housing of FIG.36.

FIG. 40 is a plan view of a valve seat of FIG. 36.

FIG. 41 is a sectional view taken along A—A line of FIG. 36.

FIG. 42 is a sectional view of a channel selector valve of FIG. 36 in acooling mode.

FIG. 43 is a sectional view of a channel selector valve of FIG. 36 in aheating mode.

FIG. 44 is a development of a cam groove of FIG. 39.

FIG. 45 is a view illustrating a relative positional relationshipbetween a main valve element and a valve seat with respect to theirdirection of rotation.

FIG. 46 is a sectional view of a channel selector valve according to asixteenth embodiment of the present invention, which can be employed asthe rotary channel selector valve of FIG. 35.

FIG. 47 is a sectional view of a channel selector valve according to aseventeenth embodiment of the present invention, which can be employedas the rotary channel selector valve of FIG. 35.

FIG. 48 is a sectional view of a channel selector valve according to aeighteenth embodiment of the present invention, which can be employed asthe rotary channel selector valve of FIG. 35.

FIG. 49 is a development of a cam groove of FIG. 48.

FIG. 50 is a sectional view of a channel selector valve of FIG. 48 in acooling mode.

FIG. 51 is a development of a cam groove of FIG. 48.

FIG. 52 is a sectional view of a channel selector valve of FIG. 48 uponswitching between a cooling and heating mode.

FIG. 53 is a sectional view of a channel selector valve of FIG. 48 in aheating mode.

FIG. 54 is a sectional view of a channel selector valve according to anineteenth embodiment of the present invention, which can be employed asthe rotary channel selector valve of FIG. 35.

FIG. 55 is a side view of a rotating central shaft of FIG. 54.

FIG. 56 is a development of a cam groove of FIG. 55.

FIG. 57 is an enlarged sectional view of a primary part of a main valveelement of FIG. 54.

FIG. 58 is a sectional view of a channel selector valve according to atwentieth embodiment of the present invention, which can be employed asthe rotary channel selector valve of FIG. 35.

FIG. 59 is a development of a cam groove of FIG. 58.

FIG. 60 is a view illustrating a schematic constitution of arefrigerating cycle employing a compressor with a channel selector valveaccording to a twenty first embodiment of the present invention.

FIG. 61 is a view illustrating a schematic constitution of arefrigerating cycle employing a compressor with a channel selector valveaccording to a twenty second embodiment of the present invention.

FIG. 62 is a block diagram according to an embodiment of a device forcontrolling a refrigerating cycle of the present invention.

FIG. 63 is a block diagram illustrating an example of a refrigeratingcycle according to an embodiment of the present invention.

FIG. 64 is a block diagram principally illustrating an electric systemof an indoor and outdoor control according to an embodiment of thepresent invention.

FIG. 65 is a block diagram illustrating a flow of signal and actionaccording to an embodiment of a device for controlling a refrigeratingcycle of the present invention.

FIG. 66 is a part of a flow chart of a main routine according to anembodiment of the present invention.

FIG. 67 is another part of a flow chart of a main routine according toan embodiment of the present invention.

FIG. 68 is a flow chart of a sub-routine for a channel selector valveaccording to the first embodiment of the present invention.

FIG. 69 is a flow chart of steps of transferring liquid refrigerantaccording to an embodiment of the present invention.

FIG. 70 is a flow chart of a sub-routine for a channel selector valveaccording to the second embodiment of the present invention.

FIG. 71 is a flow chart of a sub-routine for a channel selector valveaccording to the third embodiment of the present invention.

FIG. 72 is a flow chart of a sub-routine when a position of a capillarytube according to the third embodiment of the present invention isexchanged with that of an electrically-driven expansion valve.

FIG. 73 is a flow chart of a sub-routine for a channel selector valveaccording to the fourth embodiment of the present invention.

FIG. 74 is a flow chart of a sub-routine for a channel selector valveaccording to the fifth embodiment of the present invention.

FIG. 75 is a flow chart of a sub-routine for a channel selector valveaccording to the seventh embodiment of the present invention.

BEST MODE FOR CARRYING OUT THE INVENTION

In the following, the channel selector valve and the method of drivingthe same according to the present invention will be explained withreference to the attached drawings.

FIG. 1 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to afirst embodiment of the present invention. The channel selector valveaccording to the first embodiment constitutes a refrigerating cycle Atogether with a compressor 4, an indoor heat exchanger 9A, an outdoorheat exchanger 9B and a throttle 10 of an electrically-driven expansionvalve or a capillary tube, wherein the throttle 10 is provided betweenthe indoor heat exchanger 9A and the outdoor heat exchanger 9B.

The channel selector valve according to the first embodiment, anoperating state of which in the heating mode is shown in FIG. 1 with asectional view thereof, has a cylindrical reversing valve housing 1, toboth ends of which stoppers 2 and 3 are firmly fixed. An outlet pipe 5communicating with an outlet (not shown in the figure) of the compressor4 is connected to one side of the periphery of the reversing valvehousing 1, while an inlet pipe 6 communicating with an inlet (not shownin the figure) of the compressor 4 and two pipes 7 and 8 disposed atboth sides of the inlet pipe 6 in an axial direction of the reversingvalve housing 1 are connected to an opposite side of the periphery ofthe reversing valve housing 1, wherein the pipes 7 and 8 constitute therefrigerating cycle A together with the channel selector valve and thecompressor 4 and are connected to two heat exchangers 9A and 9B disposedindoors and outdoors, respectively, which are utilized reversibly as acondenser or an evaporator.

Inner ends of the inlet pipe 6 and the pipes 7 and 8 are connected tothree through holes 11 a, 11 b and 11 c on a selector valve seat 11firmly fixed in the reversing valve housing 1, respectively, and acontinuous smooth surface 11 d is formed on the inner side of the valveseat 11.

In the reversing valve housing 1, there is provided a piston cylinder 12(corresponding to the movable member) between the valve seat 11 and thestopper 3, which partitions the reversing valve housing 1 into a highpressure chamber R₁ (corresponding to the first pressure chamber) and apressure-transducing chamber R₂ (corresponding to the second pressurechamber). There is provided a compression spring 13 (corresponding toenergizing means) between the piston cylinder 12 and the stopper 3,thereby the piston cylinder 12 is always energized toward the highpressure chamber R₁.

On the valve seat 11, there is provided a slide valve 27 having acommunication cavity 27 a, which is joined to the piston cylinder 12 inuse of a connecting shaft 28 and slides on the smooth surface 11 d inresponse to the movement of the piston 12 in the reversing valve housing1, thereby the through hole 11 a corresponding to the inlet pipe 6alternatively communicates with the through hole 11 b or 11 c, each ofwhich puts the through hole 11 a therebetween and corresponds to therespective pipe 7 or 8 for the respective heat exchanger.

FIG. 2 is a view illustrating a schematic constitution of arefrigerating cycle, in which a sectional view of the channel selectorvalve in a cooling mode is shown.

That is, the piston cylinder 12 can move between a first position and asecond position: at said first position, the piston cylinder 12 isprevented from moving further toward the stopper 2 because an end of theconnecting shaft 28 abuts on the stopper 2 as shown in FIG. 1; and atsaid second position, the piston cylinder 12 is prevented from movingfurther toward the stopper 3 because the piston cylinder 12 abuts on thestopper 3 as shown in FIG. 2.

As shown in FIG. 1, when the piston cylinder 12 is at the firstposition, the slide valve 27 communicates the through hole 11 acorresponding to the inlet pipe 6 to the through hole 11 c correspondingto the pipe 8 through a low-pressure side closed space (hereinafter, aclosed space) S1 (corresponding to the second space), which is formed inthe high pressure chamber R₁ by the cavity 27 a and the smooth surface11 d of the valve seat 11, while the through hole 11 b corresponding tothe pipe 7 communicates with the outlet pipe 5 through a high pressureside closed space (hereinafter, a high pressure space) S2 (correspondingto the first space), which is formed in the high pressure chamber R₁ bythe slide valve 27 and isolated from the closed space S1.

Then, as shown in FIG. 2, when the piston cylinder 12 is at the secondposition, the slide valve 27 communicates the through hole 11 acorresponding to the inlet pipe 6 to the through hole 11 b correspondingto the pipe 7 through the closed space S1, while the through hole 11 ccorresponding to the pipe 8 communicates with the outlet pipe 5 throughthe high pressure space S2.

Further, an end of a channel 14 (corresponding to the communicationpipe) is connected to the stopper 3, while the opposite end of thechannel 14 is connected to the pipe 7 by way of the outside of thereversing valve housing 1, whereby the pressure-transducing chamber R₂always communicates with the pipe 7 through the channel 14.

As to the first embodiment, the reversing valve housing 1 and thestoppers 2 and 3 constitute the housing described in the claims of thisspecification, a portion of the reversing valve housing 1, to which theoutlet pipe 5 connected to the outlet of the compressor 4 is connected,corresponds to the inlet port described in the claims of thisspecification, while the through hole 11 a on the valve seat 11, towhich the inlet pipe 6 connected to the inlet of the compressor 4 isconnected, corresponds to the outlet port described in the claims ofthis specification.

Further, as to the channel selector valve according to the firstembodiment, the through holes 11 b and 11 c of the valve seat 11, towhich the pipe 7 connected to the indoor heat exchanger 9A and the pipe8 connected to the outdoor heat exchanger 9B are connected respectively,correspond to the two selector ports described in the claims of thisspecification.

In the following, an operation of the channel selector valve accordingto the first embodiment constructed as described above will beexplained.

When the operation of the compressor 4 is halted, as shown in FIG. 1,the piston cylinder 12 energized by the compression spring 13 is at thefirst position, the inlet pipe 6 communicates with the pipe 8 throughthe closed space S1, while the outlet pipe 5 communicates with the pipe7 through the high pressure space S2.

When the compressor 4 starts to operate, a refrigerant discharged fromthe compressor 4 flows into the high pressure space S2 through theoutlet pipe 5. At that time, if a force F1 (hereinafter, forward driveforce) applied to the piston cylinder 12 from the high pressure chamberR₁ due to the pressure of the refrigerant is equal to or less than theresultant force F2+Fs+Ff, the piston cylinder 12 does not move from thefirst position, wherein F2 (hereinafter, backward drive force) is theforce applied to the piston cylinder 12 from the pressure-transducingchamber R₂ due to the pressure of the refrigerant in thepressure-transducing chamber R₂, Fs is the energizing force by thecompression spring 13, and Ff is the static friction force between thesmooth surface 11 d of the valve seat 11 and the slide valve 27.

On the other hand, if the forward drive force F1 is greater than theresultant force F2+Fs+Ff, the piston cylinder 12 moves from the firstposition to the second position as shown in FIGS. 1 and 2, respectively.

If the piston cylinder 12 does not move from the first position, asshown in FIG. 1, the inlet pipe 6 keeps communicating with the pipe 8through the closed space S1, while the outlet pipe 5 keeps communicatingwith the pipe 7 through the high pressure space S2.

Then, since the pipe 7 communicating with the high pressure space S2always communicates with the pressure-transducing chamber R₂ through thechannel 14, the pressure of the refrigerant in the high pressure chamberR₁ becomes equal to that of the refrigerant in pressure-transducingchamber R₂.

Consequently, as long as the pressure of the refrigerant discharged fromthe compressor 4 is restrained so that the forward drive force F1 isequal to or less than the resultant force F2+Fs+Ff, the piston cylinder12 keeps staying at the first position, thereby the inlet pipe 6 keepscommunicating with the pipe 8 through the closed space S1, while theoutlet pipe 5 keeps communicating with the pipe 7 through the highpressure space S2.

To the contrary, when the piston cylinder 12 moves from the firstposition to the second position, as shown in FIG. 2, the outlet pipe 5communicates with the pipe 8 through the high pressure space S2, whilethe inlet pipe 6 communicates with the pipe 7 through the closed spaceS1.

Then, the pressure of the refrigerant in the high pressure chamber R₁,which becomes equal to that of the refrigerant at the outlet of thecompressor 4 since the pressure-transducing chamber R₂ alwayscommunicates with the inlet pipe 6 through the pipe 7 and the channel14, becomes greater than the pressure of the refrigerant in thepressure-transducing chamber R₂, which becomes equal to that of therefrigerant at the inlet of the compressor 4 since thepressure-transducing chamber R₂ communicates with the inlet of thecompressor 4, by a difference between an outlet pressure and an inletpressure of the refrigerant due to an operation of the compressor 4.

Consequently, as long as the pressure of the refrigerant discharged fromthe compressor 4 is kept high so that the forward drive force F1 isgreater than a force F2+Fs−Ff, the piston cylinder 12 keeps staying atthe second position, thereby the outlet pipe 5 keeps communicating withthe pipe 8 through the high pressure space S2, while the inlet pipe 6keeps communicating with the pipe 7 through the closed space S1.

Therefore, if the refrigerant, the pressure of which is such that theforward drive force F1 is equal to or less than the resultant forceF2+Fs+Ff, flows into the high pressure space S2 through the outlet pipe5 upon start of operation of the compressor 4, the piston cylinder 12 issituated at the first position as shown in FIG. 1.

To the contrary, if the refrigerant, the pressure of which is such thatthe forward drive force F1 is greater than the resultant force F2+Fs+Ff,flows into the high pressure space S2 through the outlet pipe 5 uponstart of operation of the compressor 4, the piston cylinder 12 issituated at the second position as shown in FIG. 2.

Then afterward, the pressure of the refrigerant, which is dischargedfrom the compressor and flows into the high pressure space S2 throughthe outlet pipe 5, is lowered by, for example, stopping the operation ofthe compressor 4 so that the forward drive force F1 is equal to or lessthan the force F2+Fs−Ff, the piston cylinder 12 moves from the secondposition to the first position.

Therefore, when the refrigerating cycle A is operated in the heatingmode, the number of revolution of the compressor 4 upon start of itsoperation is restrained to keep the pressure of the refrigerantdischarged from the compressor 4 low so that the forward drive force F1is equal to or less than the resultant force F2+Fs+Ff, thereby thepiston cylinder 12 is kept staying at the first position even afterstart of the operation of the compressor 4.

On the other hand, when the refrigerating cycle A is operated in thecooling mode, the number of revolution of the compressor 4 upon start ofits operation is raised to increase the pressure of the refrigerantdischarged from the compressor 4 so that the forward drive force F1 isgreater than the resultant force F2+Fs+Ff, thereby the piston cylinder12 is moved from the first position to the second position upon start ofthe operation of the compressor 4.

Then, once the piston cylinder 12 is moved to the second position, aslong as the forward drive force F1 is greater than the force F2+Fs−Ff,the piston cylinder 12 is kept staying at the second position even ifthe number of revolution of the compressor 4 is lowered, thereby therefrigerating cycle A is kept being operated in the cooling mode.

Thus, according to the first embodiment, the piston cylinder 12 thatpartitions the interior of the reversing valve housing 1 into the highpressure chamber R₁ and the pressure-transducing chamber R₂ is movedbetween the first and second positions, and the slide valve 27 joined tothe piston cylinder 12 is slided on the smooth surface 11 d of the valveseat 11, thereby the closed space S1, formed by the cavity 27 a of theslide valve 27 and the smooth surface 11 d, communicates the throughhole 11 a corresponding to the inlet pipe 6 to either the through hole11 b corresponding to the pipe 7 or the through hole 11 c correspondingto the pipe 8. In order to achieve the above operation, the followingconstitution is employed as to the channel selector valve.

That is, the channel 14 always communicates the pipe 7 to thepressure-transducing chamber R₂ outside the reversing valve housing 1,and when the piston cylinder 12 is situated at the first position, thepressure of the refrigerant in the pressure-transducing chamber R₂ isset equal to that of the refrigerant in the high pressure space S2 ofthe high pressure chamber R₁ that communicates with thepressure-transducing chamber R₂ through the pipe 7 and the channel 14,thereby the piston cylinder 12 is kept at the first position.

To the contrary, when the piston cylinder 12 is situated at the secondposition, the pressure of the refrigerant in the pressure-transducingchamber R₂ is set equal to that of the refrigerant at the inlet pipe 6that communicates with the pressure-transducing chamber R₂ through thepipe 7 and the channel 14, i.e. that of the.refrigerant at the inlet ofthe compressor 4 so that the pressure of the refrigerant in thepressure-transducing chamber R₂ is lower than that of the refrigerant inthe high pressure chamber R₁, the piston cylinder 12 is kept at thesecond position due to a difference between the pressure of therefrigerant in the high pressure chamber R₁ and that of the refrigerantin pressure-transducing chamber R₂.

Therefore, the heating mode, in which the refrigerant discharged fromthe compressor 4 is supplied to the indoor heat exchanger 9A by way ofthe pipe 7, and the cooling mode, in which the refrigerant dischargedfrom the compressor 4 is supplied to the outdoor heat exchanger 9B byway of the pipe 8, can be selected by changing the pressure of thedischarged refrigerant upon start of operation of the compressor 4 andthe selected state can be maintained without using any exclusive powersource such as an electromagnetic solenoid.

According to the first embodiment, the indoor heat exchanger 9A isconnected to the pipe 7 while the outdoor heat exchanger 9B is connectedto the pipe 8, and when the piston cylinder 12 is energized by thecompression spring 13 to be situated at the first position, the outletpipe 5 communicates with the indoor heat exchanger 9A through the highpressure space S2 and the pipe 7 while the inlet pipe 6 communicateswith the outdoor heat exchanger 9B through the closed space S1 and thepipe 8, therefore, the following advantage is obtained when therefrigerating cycle A is used mainly in the heating mode.

That is, upon start of operation of the refrigerating cycle A in thecooling mode, the pressure of the refrigerant discharged from thecompressor 4 upon start of operation of the compressor 4 is set high sothat the forward drive force F1 becomes greater than the resultant forceF2+Fs+Ff, thereby the piston cylinder 12 is moved from the firstposition to the second position.

However, when the refrigerating cycle A is started to operate in theheating mode, which is more frequently employed than the cooling mode,the piston cylinder 12 is situated at the first position, then theoperation of the refrigerating cycle A in the heating mode is started,thereafter the piston cylinder 12 is still kept being situated at thefirst position, thereby the refrigerating cycle A can be maintained inoperation in the heating mode without raising the pressure of thedischarged refrigerant upon start of operation of the compressor 4 up toas high as the pressure required upon start of operation of therefrigerating cycle A in the cooling mode. Therefore, the advantagedescribed above can be obtained.

In contrast with the first embodiment, FIG. 3 is a view illustrating aschematic constitution of a refrigerating cycle employing a channelselector valve according to a second embodiment of the presentinvention. As to the second embodiment, the outdoor heat exchanger 9B isconnected to the pipe 7 while the indoor heat exchanger 9A is connectedto the pipe 8, and when the piston cylinder 12 is energized by thecompression spring 13 to be situated at the first position, the outletpipe 5 communicates with the outdoor heat exchanger 9B through the highpressure space S2 and the pipe 7 while the inlet pipe 6 communicateswith the indoor heat exchanger 9A through the closed space S1 and thepipe 8, therefore, the following advantage is obtained when therefrigerating cycle A is used mainly in the cooling mode.

That is, upon start of operation of the refrigerating cycle A in theheating mode, the pressure of the refrigerant discharged from thecompressor 4 upon start of operation of the compressor 4 is set high sothat the forward drive force F1 becomes greater than the resultant forceF2+Fs+Ff, thereby the piston cylinder 12 is moved from the firstposition to the second position.

However, when the refrigerating cycle A is started to operate in thecooling mode, which is more frequently employed than the heating mode,the piston cylinder 12 is situated at the first position, then theoperation of the refrigerating cycle A in the cooling mode is started,thereafter the piston cylinder 12 is still kept being situated at thefirst position, thereby the refrigerating cycle A can be maintained inoperation in the cooling mode without raising the pressure of thedischarged refrigerant upon start of operation of the compressor 4 up toas high as the pressure required upon start of operation of therefrigerating cycle A in the heating mode. Therefore, the advantagedescribed above can be obtained.

As to the above channel selector valve according to the first and secondembodiments, as shown in FIG. 4 (front view) and FIG. 5 (side view), adelay chamber 14′, the inner diameter of which is larger than that ofthe channel 14, may be provided so that a period of time, required forthe refrigerant pressure in the pressure-transducing chamber R₂ to beequal to the pressure in the high pressure space S2 with which thepressure-transducing chamber R₂ communicates through the pipe 7 and thechannel 14, is made longer by another period of time required for thedelay chamber 14′ to be filled with the refrigerant when the pressure ofthe refrigerant discharged from the compressor 4 is raised so that theforward drive force F1 is higher than the resultant force F2+Fs+Ff.

The delay chamber 14′ described above gives an advantage that the pistoncylinder 12 can easily move from the first position to the secondposition since a differential pressure between the refrigerant in thehigh pressure chamber R₁ and that in the pressure-transducing chamber R₂is easily occurred because the refrigerant pressure in thepressure-transducing chamber R₂ does not increase in a short period timeeven if the refrigerant pressure in the high pressure space S2 israised.

The structure of the delay chamber 14′ is not limited to that shown inFIGS. 4 and 5, in which the delay chamber 14′ is attached to thereversing valve housing 1 by a belt 1′.

In the following, a channel selector valve according to a thirdembodiment of the present invention will be explained with reference toFIGS. 6 and 7.

FIG. 6 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to thethird embodiment of the present invention, in which the sameabbreviation numerals with those used for the corresponding identicalmembers or parts of the channel selector valve according to the firstembodiment shown in FIG. 1 are used.

The channel selector valve according to the third embodiment, a state inoperation in the hearting mode of which is shown in FIG. 6 by itssectional view, is different from the channel selector valve accordingto the first embodiment in a point that the channel 14 alwayscommunicating the pressure-transducing chamber R₂ to the pipe 7 by wayof the outside of the reversing valve housing 1 is omitted.

Furthermore, the channel selector valve according to the thirdembodiment shown in FIG. 6 is different from the channel selector valveaccording to the first embodiment shown in FIG. 1 in a point that thepiston cylinder 12 is provided with a through hole 12, (corresponding toan equalizing path), the inner diameter of which is designed in such amanner that a flow rate of the refrigerant flowing through the throughhole 12, is much smaller than that of the refrigerant flowing throughthe pipe 7 or 8, thereby the high pressure chamber R₁ alwayscommunicates with the pressure-transducing chamber R₂ through thethrough hole 12, in the reversing valve housing 1.

The channel selector valve according to the third embodiment is similarto that according to the first embodiment in points that: the housingdescribed in claims of the channel selector valve comprises thereversing valve housing 1 and the stoppers 2 and 3; a part of thereversing valve housing 1, to which the outlet pipe 5 communicating withthe outlet of the compressor 4 is connected, corresponds to the inletport described in claims; the through hole 11 a of the valve seat 11, towhich the inlet pipe 6 communicating with the inlet of the compressor 4is connected, corresponds to the outlet port described in claims; andthrough holes 11 b and 11 c of the valve seat 11, to which the pipes 7and 8 connecting with the indoor and outdoor heat exchangers 9A and 9B,respectively, are connected, correspond to the respective two selectorports described in claims.

In the following, an operation of the channel selector valve accordingto the third embodiment constructed as described above will beexplained.

As shown in FIG. 6, when the operation of the compressor 4 is halted,the piston cylinder 12 is at the first position due to the energizingforce Fs of the compression spring 13, thereby the inlet pipe 6communicates with the pipe 8 through the closed space S1 and the outletpipe 5 communicates with the pipe 7 through the high pressure space S2.

When the compressor 4 starts to operate, if the forward drive force F1is equal to or less than the resultant force F2+Fs+Ff, the pistoncylinder 12 does not move and stays at the first position, therefore theinlet pipe 6 keeps communicating with the pipe 8 through the closedspace S1 and the outlet pipe 5 keeps communicating with the pipe 7through the high pressure space S2.

In this situation, the pressure of the refrigerant in the high pressurechamber R₁ increases due to the refrigerant flowed into the highpressure space S2 from the compressor 4 through the outlet pipe 5 andexceeds the pressure of the refrigerant in the pressure-transducingchamber R₂, while the refrigerant gradually flows into thepressure-transducing chamber R₂ from the high pressure space S2 throughthe through hole 12, of the piston cylinder 12, as a result when thetime passes, the pressure of the refrigerant in the high pressure spaceS2 becomes equal to that of the refrigerant in the pressure-transducingchamber R₂.

Therefore, as long as the pressure of the refrigerant discharged fromthe compressor 4 is restrained so that the forward drive force F1 isequal to or less than the resultant force F2+Fs+Ff, the piston cyliner12 keeps staying at the first position, as a result, the outlet pipe 5keeps communicating with the pipe 7 through the high pressure space S2and the inlet pipe 6 keeps communicating with the pipe 8 through theclosed space S1.

To the contrary, when the forward drive force F1 exceeds the resultantforce F2+Fs+Ff, the piston cylinder 12 moves from the first position, asshown in FIG. 7 illustrating a schematic constitution of a refrigeratingcycle in which a sectional view of the channel selector valve in acooling mode is shown, the piston cylinder 12 abuts on the stopper 3,thereby the piston cylinder 12 is situated at the second position bybeing restricted its further movement toward the stopper 3, that is, theoutlet pipe 5 communicates with the pipe 8 through the high pressurespace S2 and the inlet pipe 6 communicates with the pipe 7 through theclosed space S1.

Thereafter, if the compressor 4 is kept in operation with keeping adifference between the high and low pressures so that the staticfriction force Ff exceeds the energizing force Fs due to the compressionspring 13, the piston cylinder 12 keeps staying at the second position.

Similarly to the function of the channel selector valve according to thefirst embodiment, by employing the channel selector valve according tothe third embodiment, the heating mode, in which the refrigerantdischarged from the compressor 4 is supplied to the indoor heatexchanger 9A by way of the pipe 7, and the cooling mode, in which therefrigerant discharged from the compressor 4 is supplied to the outdoorheat exchanger 9B by way of the pipe 8, can be selected by changing thepressure of the discharged refrigerant upon start of operation of thecompressor 4 and the selected state can be maintained without using anyexclusive power source such as an electromagnetic solenoid.

According to the third embodiment, the indoor heat exchanger 9A isconnected to the pipe 7 while the outdoor heat exchanger 9B is connectedto the pipe 8, and when the piston cylinder 12 is energized by thecompression spring 13 to be situated at the first position, the outletpipe 5 communicates with the indoor heat exchanger 9A through the highpressure space S2 and the pipe 7 while the inlet pipe 6 communicateswith the outdoor heat exchanger 9B through the closed space S1 and thepipe 8, therefore, the advantage that is the same with that of thechannel selector valve according to the first embodiment is obtainedwhen the refrigerating cycle A is used mainly in the heating mode.

In contrast with the third embodiment, FIG. 8 is a view illustrating aschematic constitution of a refrigerating cycle employing a channelselector valve according to a fourth embodiment of the presentinvention. As to the fourth embodiment, the outdoor heat exchanger 9B isconnected to the pipe 7 while the indoor heat exchanger 9A is connectedto the pipe 8, and when the piston cylinder 12 is energized by thecompression spring 13 to be situated at the first position, the outletpipe 5 communicates with the outdoor heat exchanger 9B through the highpressure space S2 and the pipe 7 while the inlet pipe 6 communicateswith the indoor heat exchanger 9A through the closed space S1 and thepipe 8, therefore, the advantage that is the same with that of thechannel selector valve according to the second embodiment is obtainedwhen the refrigerating cycle A is used mainly in the cooling mode.

As to each channel selector valve according to the first to fourthembodiments, when the compressor 4 is in operation, a pressure of therefrigerant discharged from the compressor 4 flowing into the highpressure space S2 through the outlet pipe 5 is higher than anotherpressure of the refrigerant in the closed space S1 communicating withthe inlet of the compressor 4 through the inlet pipe 6 whether thepiston cylinder 12 is at the first position or the second position,therefore, the slide valve 27 is pressed onto the valve seat 11 by aforce corresponding to a difference between these two pressures of therefrigerant.

Consequently, when the compressor 4 is in operation, a static frictionforce between the slide valve 27 and the smooth surface 11 d of thevalve seat 11 increases by a quantity corresponding to the difference inpressure between the refrigerant in the high pressure space S2 and thatin the closed space S1, which is a basis for a force to press the slidevalve 27 onto the valve seat 11.

Therefore, when the piston cylinder 12 is moved between the first andsecond positions in order to switch the operation mode of therefrigerating cycle A between the heating mode and the cooling mode,preferably, the static friction force between the slide valve 27 and thesmooth surface 11 d of the valve seat 11 is reduced or removed byreducing or removing the difference in pressure between the refrigerantin the high pressure space S2 and that in the closed space S1 through,for example, a tentative stop of the operation of the compressor 4.

In the above third or fourth embodiment, the equalizing path isconstituted by the through hole 12 ₁ of the piston cylinder 12. However,the equalizing path provided for the movable member is not limited tothe through hole described above and may be a path formed between theother member or may be constituted in combination with a path and athrough hole.

In the following, a channel selector valve according to a fifthembodiment of the present invention will be explained with reference toFIGS. 9 to 14.

FIG. 9 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to thefifth embodiment of the present invention, in which the sameabbreviation numerals with those used for the corresponding identicalmembers or parts of the channel selector valve according to the firstembodiment shown in FIG. 1 are used.

The channel selector valve according to the fifth embodiment, a state inoperation in the hearting mode of which is shown in FIG. 9 by itssectional view, constitutes the refrigerating cycle A together with thecompressor 4, the indoor heat exchanger 9A, the outdoor heat exchanger9B and the capillary tube 10B that is provided between the indoor heatexchanger 9A and the outdoor heat exchanger 9B.

The channel selector valve according to the fifth embodiment isdifferent from the channel selector valve according to the firstembodiment shown in FIG. 1 in a point that the reversing valve housing 1is provided with a latch mechanism 32 (corresponding to the latchmechanism described in claims 25 to 28) at one end thereof, whichincludes a seal housing 32 a that seals one end of the reversing valvehousing 1 instead of the stopper 3.

As to the channel selector valve according to the fifth embodiment, thepiston cylinder 12 can move between a first position and a secondposition: at said first position, the piston cylinder 12 is preventedfrom moving further toward the stopper 2 because an end of theconnecting shaft 28 abuts on the stopper 2 as shown in FIG. 9; and atsaid second position, the piston cylinder 12 is prevented from movingfurther toward the seal housing 32 a because the piston cylinder 12abuts on the seal housing 32 a as shown in FIG. 10. FIG. 10 is a viewillustrating a schematic constitution of a refrigerating cycle, in whicha sectional view of the channel selector valve of FIG. 9 in a coolingmode is shown.

The latch mechanism 32 comprises the seal housing 32 a, a guide cylinder32 c received in the seal housing 32 a, a part of which protrudes towardthe inside of the pressure-transducing chamber R₂ of the reversing valvehousing 1, a latch piece 32 k, and a coil spring 32 p.

The seal housing 32 a has a hollow cylindrical shape with one end openand the opposite end closed, as shown in FIG. 11 (an enlarged sectionalview of a primary part of a latch mechanism of FIG. 9), at a peripherynear the closed end of the seal housing 32 a, there is provided a port32 b for communicating the interior of the seal housing 32 a with theexterior thereof, to which a channel 14B connected to the inlet pipe 6is connected.

The guide cylinder 32 c consists of two layers, i.e. an outer cylinder32 d and an inner cylinder 32 e in which a cam groove 32 f for the latchaction is formed.

FIG. 12 is an enlarged development of a primary part of an innercylinder 32 e. As shown in FIG. 12, the cam groove 32 f is formed in ashape of a deformed saw blade, in which shallow grooves 32 g and deepgrooves 32 h are arranged in a circumferential direction of the innercylinder 32 e at intervals of 90° and a connection groove 32 j connectsthe shallow groove 32 g with the adjoining deep groove 32 h.

The latch piece 32 k has a flat cylindrical shape and its diameter isformed so that the latch piece 32 k is movable in an axial directionwithin the inner cylinder 32 e of the guide cylinder 32 c. At eachcircumferential position located in a circumferential direction of thelatch piece 32 k at intervals of 90°, a respective cam follower pin 32 mthat can be inserted into the cam groove 32 f of the inner cylinder 32 eis formed. Inside the latch piece 32 k, a through hole 32 n is formedthroughout both ends thereof.

The coil spring 32 p is provided between the latch piece 32 k and theclosed opposite end of the seal housing 32 a, by an elastic force ofwhich the latch piece 32 k is energized toward the open end of the sealhousing 32 a.

As to the latch mechanism 32, the cam follower pin 32 m of the latchpiece 32 k energized by the elastic force of the coil spring 32 p isguided by a first inclined plane 32 j ₁ of the connection groove 32 j ofthe cam groove 32 f so as to abut on a stopper plane 32 j ₂ so that thelatch piece 32 k is situated at a deregulation position of the innercylinder 32 e, that is, in the vicinity of the end of the inner cylinder32 e at the high pressure chamber R₁ side.

When the cam follower pin 32 m of the latch piece 32 k situated at thederegulation position abuts on the stopper plane 32 j ₂ by way of thefirst inclined plane 32 j ₁ of the connection groove 32 j facing thedeep groove 32 h, that is, when the cam follower pin 32 m is situated ata position “a” in a locus of the cam follower pin 32 m shown with animaginary lines (i.e. alternate long and short dash lines or alternatelong and two short dashes lines) in FIG. 12, the latch piece 32 k ismoved toward the closed end of the seal housing 32 a against the elasticforce by the coil spring 32 p, thereby the latch mechanism 32 performsthe following action.

That is, the cam follower pin 32 m is guided by the stopper plane 32 j ₂so as to move from the position “a” to a position “b”, then guided by asecond inclined plane 32 j ₃ of the connection groove 32 j facing thestopper plane 32 j ₂ so as to move from the position “b” to a position“c”, thereby the cam follower pin 32 m abuts on a stopper plane 32 g ₁of the shallow groove 32 g.

Then, in this state, as long as a force to move the latch piece 32 ktoward the closed end of the seal housing 32 a affects the latch piece32 k, as shown in FIG. 12, the movement of the latch piece 32 k isrestrained at a first regulation position where is a first stroke L1 offfrom the deregulation position, shown with an imaginary line (i.e.alternate long and two short dashes line) in FIG. 13, toward the closedend of the seal housing 32 a.

When the cam follower pin 32 m of the latch piece 32 k situated at thederegulation position abuts on the stopper plane 32 j ₂ by way of thefirst inclined plane 32 j ₁ of the connection groove 32 j facing theshallow groove 32 g, that is, when the cam follower pin 32 m is situatedat a position “e” in a locus of the cam follower pin 32 m shown with animaginary lines (i.e. alternate long and short dash lines or alternatelong and two short dashes lines) in FIG. 12, the latch piece 32 k ismoved toward the closed end of the seal housing 32 a against the elasticforce by the coil spring 32 p, thereby the latch mechanism 32 performsthe following action.

That is, the cam follower pin 32 m is guided by the stopper plane 32 j ₂so as to move from the position “e” to a position “f”, then guided bythe second inclined plane 32 j ₃ of the connection groove 32 j facingthe stopper plane 32 j ₂ so as to move from the position “f” to aposition “g”, thereby the cam follower pin 32 m reaches an end of thedeep groove 32 h.

Then, as long as a force to move the latch piece 32 k toward the closedend of the seal housing 32 a affects the latch piece 32 k, as shown inFIG. 14, the movement of the latch piece 32 k is restrained at a secondregulation position where is a second stroke L2 off from thederegulation position, shown with an imaginary line (i.e. alternate longand two short dashes line) in FIG. 14, toward the closed end of the sealhousing 32 a.

Here, the second stroke L2 is set a little longer than a distancebetween the first position and the second position of the pistoncylinder 12, while the first stroke L1 is set much shorter than saiddistance.

In the state that the movement of the latch piece 32 k is restrained atthe first regulation position, when a force to move the latch piece 32 ktoward the closed end of the seal housing 32 a does not affect, the camfollower pin 32 m of the latch piece 32 k energized by the elastic forceof the coil spring 32 p is guided by the first inclined plane 32 j ₁ ofthe connection groove 32 j of the cam groove 32 f so as to move from aposition “d” to a position “e” in FIG. 12 and abuts on the stopper plane32 j ₂, thereby the latch piece 32 k comes back to the deregulationposition shown in FIG. 11.

Similarly, in the state that the movement of the latch piece 32 k isrestrained at the second regulation position, when a force to move thelatch piece 32 k toward the closed end of the seal housing 32 a does notaffect, the cam follower pin 32 m of the latch piece 32 k energized bythe elastic force of the coil spring 32 p is guided by the firstinclined plane 32 j ₁ of the connection groove 32 j of the cam groove 32f so as to move from a position “h” to a position “i” in FIG. 12 andabuts on the stopper plane 32 j ₂, thereby the latch piece 32 k comesback to the deregulation position shown in FIG. 11.

Furthermore, the latch mechanism 32 is constituted so that thepressure-transducing chamber R₂ communicates with the channel 14Bthrough the port 32 b, the interior of the seal housing 32 a and thethrough hole 32 n of the latch piece 32 k no matter where the latchpiece 32 k is situated at the deregulation position, the firstregulation position or the second regulation position.

In the channel selector valve according to the fifth embodiment, asshown in FIG. 11 and so on, a pin 12 e is provided on an end of thepiston cylinder 12 at the pressure-transducing chamber R₂ side, which isformed so that an end of the pin 12 e is a little spaced from an end ofthe latch piece 32 k situated at the deregulation position thereof asshown in FIG. 11.

As to the channel selector valve according to the fifth embodiment, thereversing valve housing 1, the stopper 2 and the seal housing 32 a ofthe latch mechanism 32 constitute the housing described in claims of thepresent invention, a part of the reversing valve housing 1, to which theoutlet pipe 5 connected to the outlet of the compressor 4 is connected,corresponds to the inlet port described in claims, and the through hole11 a of the valve seat 11, to which the inlet pipe 6 connected to theinlet of the compressor 4 is connected, corresponds to the outlet portdescribed in claims.

Furthermore, as to the channel selector valve according to the fifthembodiment, through holes 11 b and 11 c of the valve seat 11, to whichthe pipes 7 and 8 connecting with the indoor and outdoor heat exchangers9A and 9B, respectively, are connected, correspond to the respective twoselector ports described in claims.

In the following, an operation of the channel selector valve accordingto the fifth embodiment constructed as described above will beexplained.

When the operation of the compressor 4 is halted, as shown in FIG. 9,the piston cylinder 12 energized by the compression spring 13 is at thefirst position, the inlet pipe 6 communicates with the pipe 8 throughthe closed space S1, while the outlet pipe 5 communicates with the pipe7 through the high pressure space S2.

In this state, although the pin 12 e of the piston cylinder 12 abuts onthe latch piece 32 k, the latch piece 32 k is energized by the coilspring 32 p to be situated at the deregulation position shown in FIG.11.

When the compressor 4 starts to operate, the refrigerant discharged fromthe compressor 4 flows into the high pressure space S2 through theoutlet pipe 5, while the refrigerant pressure in thepressure-transducing chamber R₂, which communicates with the channel 14Bthrough the port 32 b of the latch mechanism 32, the interior of theseal housing 32 a and the through hole 32 n of the latch piece 32 k,becomes equal to the refrigerant pressure in the inlet pipe 6 connectedto the channel 14B.

Therefore, the pressure of the refrigerant flowed into the high pressurespace S2 exceeds the refrigerant pressure in the pressure-transducingchamber R₂ by a difference between the discharge pressure and thesuction pressure of the refrigerant due to the compressor 4, thereby theforward drive force F1 exceeds the resultant force F2+Fs+Ff.

Consequently, the piston cylinder 12 tends to move from the firstposition to the second position in the reversing valve housing 1, thenthe pin 12 e of the piston cylinder 12 pushes the latch piece 32 k andthen, the latch piece 32 k tends to move toward the closed end of theseal housing 32 a against the energizing force by the coil spring 32 p.

Here, when the cam follower pin 32 m guided by the first inclined plane32 j ₁ of the connection groove 32 j moves from the position “d” to theposition “e” in FIG. 12, that is, when the latch piece 32 k is at thederegulation position after coming back from the first regulationposition, thereafter, the latch piece 32 k moves toward the closed endof the seal housing 32 a while the cam follower pin 32 m is guided bythe second inclined plane 32 j ₃ to reach the position “g”, i.e. the endof the deep groove 32 h, by way of the position “e” and the position “f”in FIG. 12, thereby the latch piece 32 k reaches the second regulationposition as shown in FIG. 14.

Therefore, a move stroke of the latch piece 32 k toward the closed endof the seal housing 32 a becomes equal to the second stroke L2, as aresult, the piston cylinder 12 reaches the second position after leavingthe first position as shown in FIG. 10.

On the other hand, when the cam follower pin 32 m guided by the firstinclined plane 32 j ₁ of the connection groove 32 j moves from theposition “h” to the position “i” in FIG. 12, that is, when the latchpiece 32 k is at the deregulation position after coming back from thesecond regulation position, thereafter, the latch piece 32 k movestoward the closed end of the seal housing 32 a while the cam followerpin 32 m is guided by the second inclined plane 32 j ₃ to move from theposition “b” in FIG. 12 to the position “c” where the cam follower pin32 m abuts on the stopper plane 32 g ₁ of the shallow groove 32 g,thereby the movement of the latch piece 32 k is restrained at the firstregulation position as shown in FIG. 13.

Therefore, a move stroke of the latch piece 32 k toward the closed endof the seal housing 32 a becomes equal to the first stroke L1, as aresult, even if the piston cylinder 12 tends to move from the firstposition thereof, the movement of the piston cylinder 12 is restrainedby the latch piece 32 k, the movement of which is restrained at thefirst regulation position, thereby the piston cylinder 12 hardly movesand keeps staying at the first position as shown in FIG. 9.

That is, the latch piece 32 k, restrained its movement toward the closedend of the seal housing 32 a at the first regulation position,substantially keeps the piston cylinder 12 that pushes the latch piece32 k by the pin 12 e from moving toward the second position, i.e. keepsthe piston cylinder 12 staying at the first position, therefore, theoutlet pipe 5 keeps communicating with the pipe 7 through the highpressure space S2 while the inlet pipe 6 keeps communicating with thepipe 8 through the closed space S1.

To the contrary, when the piston cylinder 12 reaches the second positionafter pushing the latch piece 32 k up to the second regulation positionby the pin 12 e, as shown in FIG. 10, the outlet pipe 5 communicateswith the pipe 8 through the high pressure space S2 while the inlet pipe6 communicates with the pipe 7 through the closed space S1.

When the compressor 4 starts to operate, the piston cylinder 12 thattends to move from the first position to the second position pushes thelatch piece 32 k, which comes back to the deregulation position from thesecond regulation position, by a pin 12 e toward the closed end of theseal housing 32 a, as shown in FIG. 13, the movement of the latch piece32 k is restrained at the first regulation position by the latchmechanism 32, therefore, the piston cylinder 12 hardly moves toward thesecond position and keeps staying at the first position as shown in FIG.9.

Thereafter, the pressure of the refrigerant, which is discharged fromthe compressor 4 and flows into the high pressure space S2 through theoutlet pipe 5, is reduced by stopping the operation of the compressor 4or the like so that the forward drive force F1 is equal to or less thanthe force F2+Fs−Ff, the latch piece 32 k situated at the firstregulation position moves toward the high pressure chamber R₁ by anenergizing force due to the coil spring 32 p and comes back to thederegulation position as shown in FIG. 11.

On the other hand, when the compressor 4 starts to operate, the pistoncylinder 12 that tends to move from the first position to the secondposition pushes the latch piece 32 k, which is at the deregulationposition after coming back from the first regulation position, by a pin12 e toward the closed end of the seal housing 32 a, as shown in FIG.14, the latch piece 32 k reaches the second regulation position,therefore, the piston cylinder 12 reaches the second position as shownin FIG. 10.

Thereafter, the pressure of the refrigerant, which is discharged fromthe compressor 4 and flows into the high pressure space S2 through theoutlet pipe 5, is reduced by stopping the operation of the compressor 4or the like so that the forward drive force F1 is equal to or less thanthe force F2+Fs−Ff, the latch piece 32 k situated at the secondregulation position moves toward the high pressure chamber R₁ by anenergizing force due to the coil spring 32 p and comes back to thederegulation position as shown in FIG. 11.

Therefore, when the refrigerating cycle A is operated in the heatingmode, the latch piece 32 k can be set at the deregulation position aftercoming back from the second regulation position, then the compressor 4is started to operate, thereby the piston cylinder 12 can be kept at thefirst position during the operation of the compressor 4.

On the other hand, when the refrigerating cycle A is operated in thecooling mode, the latch piece 32 k can be set at the deregulationposition after coming back from the first regulation position, then thecompressor 4 is started to operate, thereby the piston cylinder 12 canbe moved from the first position to the second position immediatelyafter the operation of the compressor 4.

Once the piston cylinder 12 finishes to move to the second position, aslong as the forward drive force F1 exceeds the force F2+Fs−Ff, thepiston cylinder 12 is kept staying at the second position even if thenumber of revolution of the compressor 4 is reduced, thereby therefrigerating cycle A is kept operating in the cooling mode.

Thus, in the fifth embodiment, the pressure-transducing chamber R₂ ofthe reversing valve housing 1 always communicates with the inlet pipe 6,and the move stroke of the latch piece 32 k, which is pushed by a pin 12e of the piston cylinder 12 that moves from the first position to thesecond position, is set to be either the second stroke L2 correspondingto the second regulation position, which allows the piston cylinder 12to reach the second position, or the first stroke L1 corresponding tothe first regulation position, which does not allow the piston cylinder12 to reach the second position, with being alternately controlled bythe latch mechanism 32.

The latch piece 32 k can be set at the deregulation position aftercoming back from the second regulation position, then the compressor 4is started to operate, thereby the piston cylinder 12 can be kept at thefirst position. Further, the latch piece 32 k can be set at thederegulation position after coming back from the first regulationposition, then the compressor 4 is started to operate, thereby thepiston cylinder 12 can be moved from the first position to the secondposition, and thereafter, the piston cylinder 12 can be kept at thesecond position as long as the operation of the compressor 4 is nothalted.

Therefore, the heating mode, in which the refrigerant discharged fromthe outlet pipe 5 is supplied to the indoor heat exchanger 9A by way ofthe pipe 7, and the cooling mode, in which the refrigerant dischargedfrom the outlet pipe 5 is supplied to the outdoor heat exchanger 9B byway of the pipe 8, can be selected by controlling the number of times ofthe operation start of the compressor 4 and the selected state can bemaintained without using any exclusive power source such as anelectromagnetic solenoid.

In contrast with the fifth embodiment, FIG. 15 is a view illustrating aschematic constitution of a refrigerating cycle employing a channelselector valve according to a sixth embodiment of the present invention.As to the sixth embodiment, the outdoor heat exchanger 9B is connectedto the pipe 7 while the indoor heat exchanger 9A is connected to thepipe 8, and when the piston cylinder 12 is restrained by the latchmechanism 32 and situated at the first position, the outlet pipe 5communicates with the outdoor heat exchanger 9B through the highpressure chamber R₁ and the pipe 7 while the inlet pipe 6 communicateswith the indoor heat exchanger 9A through the closed space S1 and thepipe 8.

The latch mechanism 32 is not limited to such a mechanism that the latchpiece 32 k alternately moves between the second and first regulationpositions by way of the deregulation position as described above,instead, a mechanism in which the second and first regulation positionsare randomly selected by using a torque driver may be employed.

FIG. 16 is a view illustrating a schematic constitution of a latchmechanism usable instead of the latch mechanism described above. FIG. 17is a development of a cam groove, along which a cam follower pin of FIG.16 moves. As shown in FIG. 16, an end 12 a of the pin 12 e of the pistoncylinder 12 is inserted into a bearing 32 r of the latch piece 32 k soas to rotatively connect the latch piece 32 k with the pin 12 e, and asshown in FIG. 17, the cam groove 32 f, along which the cam follower pin32 m of the latch piece 32 k moves, is formed as a limited path inclinedwith respect to an axial direction of the inner cylinder 32 e, therebyforming the shallow groove 32 g in the middle of the limited path andthe deep groove 32 h at an end of the limited path.

With the construction mentioned above, the pressure of the refrigerant,which is discharged from the compressor 4 and flows into the highpressure space S2 through the outlet pipe 5, is raised so as to increasea moving rate of the piston cylinder 12 from the first position to thesecond position, then the latch piece 32 k has a large rotation momentand then, the cam follower pin 32 m reaches the deep groove 32 h at theend of the cam groove 32 f after passing through the shallow groove 32g, thereby the piston cylinder 12 is situated at the second position.

On the contrary, the pressure of the refrigerant, which is dischargedfrom the compressor 4 and flows into the high pressure space S2 throughthe outlet pipe 5, is reduced so as to decrease a moving rate of thepiston cylinder 12 from the first position to the second position, thenthe latch piece 32 k has only a small rotation moment and then, the camfollower pin 32 m cannot pass through the shallow groove 32 g and staysat the shallow groove 32 g, thereby the piston cylinder 12 stays at thefirst position since its movement toward the second position isrestrained.

Then, whether the cam follower pin 32 m is situated at either theshallow groove 32 g or the deep groove 32 h, when the operation of thecompressor 4 is halted, the latch piece 32 k comes back to its originalposition (i.e. a light end of its locus in FIG. 17) due to an energizingforce by the coil spring 32 p, thereafter, when the compressor 4 isstarted to operate, the cam follower pin 32 m can move to either theshallow groove 32 g or the deep groove 32 h depending upon the pressureof the discharged refrigerant.

With the construction mentioned above, the piston cylinder 12 can besituated at the desired position out of the first and second positionsonly by increasing or decreasing the pressure of the refrigerantdischarged from the compressor 4, furthermore, when the cam follower pin32 m is moved from the shallow groove 32 g to the deep groove 32 h orfrom the deep groove 32 h to the shallow groove 32 g, the operation ofthe compressor 4 is neither needed to be started nor needed to be haltedin order to rotate the latch piece 32 k for resetting the presentposition, resulting in an advantage for the operation.

In the following, a channel selector valve according to a seventhembodiment of the present invention will be explained with reference toFIGS. 18 to 22.

FIG. 18 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to theseventh embodiment of the present invention, in which the sameabbreviation numerals with those used for the corresponding identicalmembers or parts of the refrigerating cycle according to the fifthembodiment shown in FIG. 9 are used.

The channel selector valve according to the seventh embodiment, a statein operation in the hearting mode of which is shown in FIG. 18 by itssectional view, is different from the channel selector valve accordingto the fifth embodiment shown in FIG. 9 in a point that instead of thelatch mechanism 32, there is provided a pilot valve mechanism 33 havinganother latch mechanism 34 (corresponding to the second latch mechanismdescribed in claims 29 and 30), a constitution of which is similar tothe latch mechanism 32, and the stopper 3 instead of the seal housing 32a of the latch mechanism 32 seals one end of the reversing valve housing1.

FIG. 19 is an enlarged sectional view of a primary part of the pilotvalve mechanism of FIG. 18. As shown in FIG. 19, the pilot valvemechanism 33 comprises: a diaphragm 33 a for partitioning the interiorof the pressure-transducing chamber R₂ into a main chamber R₃ near thehigh pressure chamber R₁ for allowing the piston cylinder 12 to movebetween the first and second positions and a sub chamber R₄ near thestopper 3; a valve block 33 b integrally formed with the diaphragm 33 a;a pilot valve element 33 e (corresponding to the pilot valve describedin claim 29) received into the valve block 33 b; a bellows 33 g disposedin the sub chamber R₄; and a pin 33 h for retracting (i.e. for openingor closing) the pilot valve element 33 e.

In the interior of the valve block 33 b, there are provided a pilot path33 c with its one end open to the sub chamber R₄ and an open path 33 dbeing open to the main chamber R₃ extending from the opposite end of thepilot path 33 c to a circumferential surface of the valve block 33 b,while the pilot valve element 33 e is disposed at a crossing between thepilot path 33 c and the open path 33 d and energized by the coil spring33 f from the opposite end of the pilot path 33 c toward the one endthereof so as to close the pilot path 33 c.

The bellows 33 g is fixed on an inner face of the stopper 3 at one endthereof and expands or contracts so as to allow an opposite end thereofto move nearer to or away from the diaphragm 33 a or the valve block 33b. The bellows 33 g partitions the interior space of the sub chamber R₄into a first space R₄₁ (i.e. a space inside of the bellows 33 g) and asecond space R₄₂ (i.e. a space outside of the bellows 33 g).

The first space R₄₁ always communicates with the outlet pipe 5 through achannel 14D connected from the outside of the reversing valve housing 1by way of the stopper 3 and one end of the bellows 33 g, while thesecond space R₄₂ always communicates with the inlet pipe 6 through achannel 14B connected from the outside of the reversing valve housing 1by way of the stopper 3.

The pin 33 h arises from a plate 33 j fixed at the opposite end of thebellows 33 g and inserted into the pilot path 33 c from an end thereof.

Although the latch mechanism 34 is not shown in detail in FIGS. 18 and19, it comprises elements corresponding to the guide cylinder 32 c, thelatch piece 32 k and the coil spring 32 p of the latch mechanism 32 ofthe channel selector valve according to the fifth and sixth embodiments.In detail, an element corresponding to the guide cylinder 32 c of thelatch mechanism 32 is formed near one end of the valve block 33 b, whilean element corresponding to the coil spring 32 p of the latch mechanism32 is not shown in FIGS. 18 and 19.

The latch piece 34 a of the latch mechanism 34 of the seventhembodiment, which corresponds to the latch piece 32 k of the latchmechanism 32, is formed slidable with respect to the one end of thevalve block 33 b, wherein a deregulation position of the latch piece 34a is a position where the latch piece 34 a protrudes from the one end ofthe valve block 33 b toward the sub chamber R₄ as shown in FIG. 19,while a second regulation position of the latch piece 34 a is a positionwhere the latch piece 34 a is moved from the deregulation position,shown in FIG. 20 with imaginary lines (alternate long and two shortdashes lines), toward the one end of the valve block 33 b by a secondstroke L2, that is, where an end face of the latch piece 34 a is thesame plane with that of the one end of the valve block 33 b, as shown inFIG. 20.

As shown in FIG. 21, a first regulation position of the latch piece 34 ais a position where the latch piece 34 a is moved from the deregulationposition, shown in FIG. 21 with imaginary lines (alternate long and twoshort dashes lines), toward the one end of the valve block 33 b by afirst stroke L1, which is shorter than the second stroke L2, that is,where an end face of the latch piece 34 a is a little shifted from thederegulation position toward the one end of the valve block 33 b.

In the pilot valve mechanism 33 with the latch mechanism 34 constructedas describe above, when the bellows 33 g is compressed, the end face ofthe latch piece 34 a situated at the deregulation position abuts on theplate 33 j and the pin 33 h is apart from the pilot valve element 33 e,thereby the pilot path 33 c is closed by the pilot valve element 33 e.

In the pilot valve mechanism 33., when the bellows 33 g expands and theplate 33 j pushes the latch piece 34 a situated at the deregulationposition and also when the latch piece 34 a has come back to thederegulation position from the second regulation position, the latchpiece 34 a pushed by the plate 33 j is kept from moving further at thefirst regulation position where the latch piece 34 a has moved from thederegulation position toward the one end of the valve block 33 b by thefirst stroke, that is, the pin 33 h of the plate 33 j, the move of whichis restrained by the latch piece 34 a situated at the first regulationposition, is kept being apart from the pilot valve element 33 e, therebythe pilot path 33 c is kept closed by the pilot valve element 33 e.

Further, in the pilot valve mechanism 33, when the bellows 33 g expandsand the plate 33 j pushes the latch piece 34 a situated at thederegulation position and also when the latch piece 34 a has come backto the deregulation position from the first regulation position, thelatch piece 34 a pushed by the plate 33 j reaches the second regulationposition where the latch piece 34 a is moved from the deregulationposition toward the one end of the valve block 33 b by the second strokeL2, then the pin 33 h of the plate 33 j comes in contact with the pilotvalve element 33 e, allowing the pilot valve element 33 e to be apartfrom the opposite end of the pilot path 33 c by overcoming an energizingforce due to the coil spring 33 f, thereby the pilot path 33 c is openedby the pilot valve element 33 e.

As shown in FIG. 19, in the channel selector valve according to theseventh embodiment, the diaphragm 33 a of the pilot valve mechanism 33receives an end of a compression spring 13 instead of the seal housing32 a of the fifth or sixth embodiment.

In the channel selector valve according to the seventh embodiment, thepilot path described in claim 29 consists of the pilot path 33 c and theopen path 33 d, while the valve opener described in claim 29 consists ofthe pin 33 h and the plate 33 j.

Further, the channel selector valve according to the seventh embodimentis constituted similarly to that according to the fifth embodiment shownin FIG. 9, except the points mentioned above, while the channel selectorvalve according to the seventh embodiment is different from thataccording to the fifth embodiment in a point that the housing describedin claims consists of the reversing valve housing 1 and the stoppers 2and 3.

In addition, the channel selector valve according to the seventhembodiment is similar to that according to the fifth embodiment inpoints that: a part of the reversing valve housing 1, to which theoutlet pipe 5 communicating with the outlet of the compressor 4 isconnected, corresponds to the inlet port described in claims; thethrough hole 11 a of the valve seat 11, to which the inlet pipe 6communicating with the inlet of the compressor 4 is connected,corresponds to the outlet port described in claims; and through holes 11b and 11 c of the valve seat 11, to which the pipes 7 and 8 connectingwith the indoor and outdoor heat exchangers 9A and 9B, respectively, areconnected, correspond to the respective two selector ports described inclaims.

In the following, an operation of the channel selector valve accordingto the seventh embodiment constructed as described above will beexplained.

When the operation of the compressor 4 is halted, as shown in FIG. 18,the piston cylinder 12 energized by the compression spring 13 issituated at the first position, the inlet pipe 6 communicates with thepipe 8 through the closed space S1, and the outlet pipe 5 communicateswith the pipe 7 through the high pressure space S2.

In this situation, the pilot valve element 33 e energized by the coilspring 33 f closes the pilot path 33 c, therefore, the main chamber R₃of the pressure-transducing chamber R₂ does not communicate with the subchamber R₄.

When the compressor 4 starts to operate, the refrigerant discharged fromthe compressor 4 flows into the high pressure space S2 through theoutlet pipe 5, then a pressure of an inner space of the bellows 33 gcommunicating with the outlet pipe 5 through the channel 14D, that is,an inner pressure of the first space R₄₁, becomes equal to the pressureof the refrigerant in the outlet pipe 5, while an inner pressure of thesecond space R₄₂ becomes equal to the pressure of the refrigerant in theinlet pipe 6, with which the second space R₄₂ communicates through thechannel 14B.

Then, since the inner pressure of the first space R₄₁ exceeds that ofthe second space R₄₂, the bellows 33 g expands, then the plate 33 jmoves toward the diaphragm 33 a in the sub chamber R₄ so as to reducethe second space R₄₂, thereby the plate 33 j moves the latch piece 34 a,situated at the deregulation position and protruding toward the insideof the sub chamber R₄ from the diaphragm 33 a, in a retreating directionfrom the inside of the sub chamber R₄ as shown in FIG. 19.

At this time, if the movement of the latch piece 34 a by the plate 33 jtakes place after the latch pieced 34 a has come back from the firstregulation position to the deregulation position, the movement of thelatch piece 34 a in the retreating direction is restrained at the secondregulation position by the latch mechanism 34, therefore, a stroke ofthe latch piece 34 a in the retreating direction becomes equal to thesecond stroke L2.

As a result, as shown in FIG. 20, the pin 33 h, connected to the plate33 j and inserted into the pilot path 33 c, comes in contact with thepilot valve element 33 e, then the pilot valve element 33 e is movedbeing apart from the opposite end of the pilot path 33 c by overcomingan energizing force due to the coil spring 33 f, thereby the pilot path33 c opens.

As a result, the main chamber R₃ communicates with the second space R₄₂of the sub chamber R₄ through the pilot path 33 c and the open path 33d, then the main chamber R₃ communicates with the inlet pipe 6, whichalways communicates with the second space R₄₂, thereby an inner pressureof the main chamber R₃ becomes equal to the pressure of the refrigerantin the inlet pipe 6, which is much lower than the pressure of therefrigerant flowed into the high pressure space S2.

Therefore, the pressure of the refrigerant in the main chamber R₃ of thepressure-transducing chamber R₂ becomes less than the pressure of therefrigerant in the high pressure chamber R₁, then the piston cylinder 12moves from the first position to the second position in the main chamberR₃ as shown in FIG. 22 (cooling mode), wherein the outlet pipe 5communicates with the pipe 8 through the high pressure space S2, whilethe inlet pipe 6 communicates with the pipe 7 through the closed spaceS1.

To the contrary, if the movement of the latch piece 34 a in theretreating direction by the plate 33 j takes place after the latchpieced 34 a has come back from the second regulation position to thederegulation position, the movement of the latch piece 34 a in theretreating direction is restrained at the first regulation position,therefore, a stroke of the latch piece 34 a in the retreating directionbecomes equal to the first stroke L1.

As a result, as shown in FIG. 21, since the pin 33 h can not come intocontact with the pilot valve element 33 e and is kept apart therefrom,the pilot valve element 33 e keeps closing the pilot path 33 c due tothe energizing force by the coil spring 33 f, therefore, the mainchamber R₃ is kept insulated from the second space R₄₂ of the subchamber R₄ and the piston cylinder 12 is kept staying at the firstposition, thereby the outlet pipe 5 communicates with the pipe 7 throughthe high pressure space S2, while the inlet pipe 6 communicates with thepipe 8 through the closed space S1.

That is, when the latch piece 34 a, which has come back to thederegulation position from the second regulation position, is moved inthe retreating direction due to the movement of the plate 33 j uponstarting of the operation of the compressor 4, as shown in FIG. 21, themovement of the latch piece 34 a is restrained at the first regulatingposition due to the latch mechanism 34, then the pilot valve element 33e energized by the coil spring 33 f closes the pilot path 33 c, therebythe piston cylinder 12 keeps staying at the first position as shown inFIG. 18.

Thereafter, the inner pressure of the first space R₄₁, exceeding theinner pressure of the second space R₄₂ of the sub chamber R₄, is reducedso as to be close to the inner pressure of the second space R₄₂, bytentatively halting the operation of the compressor 4 and the like,thereby the first space R₄₁ is reduced and the second space R₄₂ isexpanded. As a result, as shown in FIG. 19, the latch piece 34 asituated at the first regulation position by the plate 33 j advancesinto the inside of the sub chamber R₄ and comes back to the deregulationposition, while the plate 33 j is moved in the direction away from thediaphragm 33 a by the latch piece 34 a.

To the contrary, when the latch piece 34 a, which has come back to thederegulation position from the first regulation position, is moved inthe retreating direction due to the movement of the plate 33 j uponstarting of the operation of the compressor 4, the movement of the latchpiece 34 a is restrained only at the second regulating position,therefore, the pilot valve element 33 e is moved in the direction awayfrom the opposite end of the pilot path 33 c by the pin 33 h connectedto the plate 33 j, by overcoming the energizing force due to the coilspring 33 f, thereby the pilot path 33 c is opened and the pistoncylinder 12 is situated at the second position as shown in FIG. 22.

Again thereafter, the inner pressure of the first space R₄₁, exceedingthe inner pressure of the second space R₄₂ of the sub chamber R₄, isreduced so as to be close to the inner pressure of the second space R₄₂,by tentatively halting the operation of the compressor 4 and the like,thereby the first space R₄₁ is reduced and the second space R₄₂ isexpanded. As a result, as shown in FIG. 19, the latch piece 34 asituated at the second regulation position by the plate 33 j advancesinto the inside of the sub chamber R₄ and comes back to the deregulationposition, while the plate 33 j is moved in the direction away from thediaphragm 33 a by the latch piece 34 a.

Then, the pin 33 h connected to the plate 33 j is apart from the pilotvalve element 33 e and then, the pilot valve element 33 e, which hasbeen moved in the direction away from the opposite end of the pilot path33 c by the pin 33 h, closes the pilot path 33 c by the energizing forcedue to the coil spring 33 f, thereby the piston cylinder 12 moves fromthe second position to the first position as shown in FIG. 18.

The channel selector valve according to the seventh embodimentconstracted as described above gives a similar effect with that of thechannel selector valve according to the fifth embodiment.

In contrast with the seventh embodiment, FIG. 23 is a view illustratinga schematic constitution of a refrigerating cycle employing a channelselector valve according to a eighth embodiment of the presentinvention. As to the eighth embodiment, the outdoor heat exchanger 9B isconnected to the pipe 7 while the indoor heat exchanger 9A is connectedto the pipe 8, and when the piston cylinder 12 is restrained by thelatch mechanism 32 and situated at the first position, the outlet pipe 5communicates with the outdoor heat exchanger 9B through the highpressure space S2 and the pipe 7 while the inlet pipe 6 communicateswith the indoor heat exchanger 9A through the closed space S1 and thepipe 8.

In the following, a channel selector valve, in which the channel isselected by controlling an opening ratio of an electrically-drivenexpansion valve, according to a ninth embodiment of the presentinvention will be explained with reference to FIGS. 24 to 27.

FIG. 24 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to theninth embodiment of the present invention, in which the sameabbreviation numerals with those used for the corresponding identicalmembers or parts of the refrigerating cycle according to the firstembodiment shown in FIG. 1 are used.

The channel selector valve according to the ninth embodiment, a state inoperation in the hearting mode of which is shown in FIG. 24 by itssectional view, constitutes the refrigerating cycle A together with thecompressor 4, the indoor heat exchanger 9A, the outdoor heat exchanger9B, an electrically-driven expansion valve 10A and a capillary tube 10B,wherein the electrically-driven expansion valve 10A and the capillarytube 10B are provided between the indoor heat exchanger 9A and theoutdoor heat exchanger 9B.

The channel selector valve according to the ninth embodiment isdifferent from that according to the first embodiment shown in FIG. 1 ina point that a part of a housing 29 a of a state-holding selector valve29 is inserted into the inside of the reversing valve housing 1 througha stopper 3 that seals one end of the reversing valve housing 1.

In the channel selector valve according to the ninth embodiment, asshown in FIG. 25, i.e. a view illustrating a schematic constitution of arefrigerating cycle in which a sectional view of the channel selectorvalve of FIG. 24 in a cooling mode is shown, the piston cylinder 12 canmove between a second position where the piston cylinder abuts on thestopper 3 to be restrained from moving further toward the stopper 3 anda first position where an end of a connecting shaft 28 abuts on astopper 2 so that the piston cylinder 12 is restrained from movingfurther toward the stopper 2.

As shown in FIG. 24, the state-holding selector valve 29 comprises thehousing 29 a, a selector valve element 29 e received in the housing 29 a(corresponding to the second selector valve element) and a coil spring29 k (corresponding to energizing means for energizing the selectorvalve).

As shown in FIG. 26, the housing 29 a has a cylindrical shape with itsone end closed and an open end of the housing 29 a is inserted into theinside of the pressure-transducing chamber R₂ of the reversing valvehousing 1, and a first port 29 b for communicating the interior of thehousing 29 a to the exterior thereof is provided near the closed end ofthe housing 29 a.

The first port 29 b is connected to a channel 14A from the outside ofthe housing 29 a and as shown in FIG. 24, the channel 14A is connectedto a position situated between the electrically-driven expansion valve10A and the capillary tube 10B.

As shown in FIG. 26, a second port 29 c for communicating the interiorof the housing 29 a to the exterior thereof is provided at a positionwhere is a little nearer to the stopper 2 than the position of the firstport 29 b.

The second port 29 c is connected to a channel 14B from the outside ofthe housing 29 a and as shown in FIG. 24, the channel 14B is connectedto an inlet pipe 6.

Further, as shown in FIG. 26, a third port 29 d for communicating theinterior of the housing 29 a to the pressure-transducing chamber R₂ isprovided at the same circumferential position with that of the secondport 29 c.

The selector valve element 29 e has an outer diameter corresponding toan inner diameter of the housing 29 a, a pin 29 f is formed at an end ofthe selector valve element 29 e, and the pin 29 f passes through astopper ring 29 g engaged with the housing 29 a and protrudes toward theoutside of an open end of the housing 29 a.

Further, a ring-shaped groove 29 h is formed on a circumferentialsurface of the selector valve element 29 e and a through hole 29 j isformed passing through the inside of the selector valve element 29 e andthe pin 29 f.

One end of the coil spring 29 k is inserted into the through hole 29 jof the selector valve element 29 e and locked at a level difference inthe through hole 29 j, while an opposite end of the coil spring 29 k isabuts on the closed end of the housing 29 a. The coil spring 29 kenergizes the selector valve element 29 e toward a direction in which alevel difference between the selector valve element 29 e and the pin 29f abuts on the stopper ring 29 g, that is, a direction in which theselector valve element 29 e protrudes toward the pressure-transducingchamber R₂ from the open end of the housing 29 a.

As to the state-holding selector valve 29, in a first state that thelevel difference between the selector valve element 29 e and the pin 29f abuts on the stopper ring 29 g due to the energizing force by the coilspring 29 k, the selector valve element 29 e is situated at a positionwhere is nearer to the open end of the housing 29 a than the first port29 b, the first port 29 b communicates with the pressure-transducingchamber R₂ through the through hole 29 j, and the ring-shaped groove 29h connects only to the third port 29 d so that the second port 29 c isclosed by the circumferential surface of the selector valve element 29e.

Further, as to the state-holding selector valve 29, as shown in FIG. 27,in a second state that the level difference between the selector valveelement 29 e and the pin 29 f is apart from the stopper ring 29 g towardthe closed end of the housing 29 a, the first port 29 b is closed by thecircumferential surface of the selector valve element 29 e, thering-shaped groove 29 h connectes to both the second port 29 c and thethird port 29 d so that the second port 29 c communicates with thepressure-transducing chamber R₂ through the ring-shaped groove 29 h andthe third port 29 d.

In the following, an operation of the channel selector valve accordingto the ninth embodiment constracted as described above will beexplained.

When the operation of the compressor 4 is halted, as shown in FIG. 24,the piston cylinder 12 is situated at the first position by energizingthe compression spring 13, then the inlet pipe 6 communicates with thepipe 8 through the closed space S1 while the outlet pipe 5 communicateswith the pipe 7 through the high pressure space S2.

This situation corresponds to the first state of the state-holdingselector valve 29, in which the selector valve element 29 e is energizedby the coil spring 29 k so that the channel 14A communicates with thepressure-transducing chamber R₂ through the first port 29 b, then thepressure-transducing chamber R₂ communicates with a position situatedbetween the electrically-driven expansion valve 10A and the capillarytube 10B in the refrigerating cycle A, to which the channel 14A isconnected.

Therefore, when the compressor 4 starts to operate, if the refrigerantpressure, at the position situated between the electrically-drivenexpansion valve 10A and the capillary tube 10B in the refrigeratingcycle A, is much the same with the pressure of the refrigerant flowedinto the high pressure space S2, that is, if the forward drive force F1is equal to or less than the resultant force F2+Fs+Ff, the pistoncylinder 12 stays at the first position.

Then, since the piston cylinder 12 stays at the first position, as shownin FIG. 26, the selector valve element 29 e is kept to be energized bythe coil spring 29 k, as a result, the state-holding selector valve 29keeps its first state, in which the pressure-transducing chamber R₂communicates with the channel 14A.

Therefore, even after the compressor 4 starts to operate, as long as thepressure of the refrigerant discharged from the compressor 4 and therefrigerant pressure at the position situated between theelectrically-driven expansion valve 10A and the capillary tube 10B areset so that the forward drive force F1 is equal to or less than theresultant force F2+Fs+Ff, the piston cylinder 12 keeps staying at thefirst position, as a result, the inlet pipe 6 keeps communicating withthe pipe 8 through the closed space S1 while the outlet pipe 5 keepscommunicating with the pipe 7 through the high pressure space S2.

To the contrary, if the refrigerant pressure, at the position situatedbetween the electrically-driven expansion valve 10A and the capillarytube 10B in the refrigerating cycle A, is much lower than the pressureof the refrigerant flowed into the high pressure space S2, that is, ifthe forward drive force F1 exceeds the resultant force F2+Fs+Ff, thepiston cylinder 12 moves from the first position and situated at thesecond position as shown in FIG. 25.

When the piston cylinder 12 moves to the second position, the pistoncylinder 12 pushes the pin 29 f toward the closed end of the housing 29a, as shown in FIG. 27, the selector valve element 29 e is in selectingoperation by the pin 29 f against the energizing force due to the coilspring 29 k, then the state-holding selector valve 29 is changed to bein the second state in which the pressure-transducing chamber R₂communicates with the channel 14B from the first state in which thepressure-transducing chamber R₂ communicates with the channel 14A.

Then, the pressure-transducing chamber R₂ communicates with the inletpipe 6 to which the channel 14B is connected and the refrigerantpressure in the pressure-transducing chamber R₂ becomes equal to thepressure of the refrigerant in the inlet pipe 6, which is much lowerthan the pressure of the refrigerant flowed into the high pressure spaceS2.

Therefore, the refrigerant pressure in the high pressure chamber R₁exceeds the refrigerant pressure in the pressure-transducing chamber R₂by a difference between the refrigerant pressure in the outlet pipe 5and the refrigerant pressure in the inlet pipe 6, thereby the pistoncylinder 12 keeps staying at the second position.

Then, since the piston cylinder 12 keeps staying at the second position,through the selecting operation of the selector valve element 29 eagainst the energizing force due to the coil spring 29 k, by the pin 29f pushed by the piston cylinder 12, the state-holding selector valve 29is maintained in the second state, in which the pressure-transducingchamber R₂ communicates with the channel 14B.

That is, when the compressor 4 starts to operate, if the refrigerantpressure, at the position situated between the electrically-drivenexpansion valve 10A and the capillary tube 10B in the refrigeratingcycle A, is set so that the resultant force F2+Fs+Ff is equal to or morethan the forward drive force F1, as shown in FIG. 24, the pistoncylinder 12 keeps staying at the first position and the state-holdingselector valve 29 is maintained in the first state.

To the contrary, when the compressor 4 starts to operate, if therefrigerant pressure, at the position situated between theelectrically-driven expansion valve 10A and the capillary tube 10B inthe refrigerating cycle A, is set so that the resultant force F2+Fs+Ffis less than the forward drive force F1, as shown in FIG. 25, the pistoncylinder 12 moves from the first position to the second position and thestate-holding selector valve 29 is changed from the first state to thesecond state, thereby the piston cylinder 12 is kept staying at thesecond position.

Thereafter, the pressure of the refrigerant, which is discharged fromthe compressor 4 and flows into the high pressure space S2 through theoutlet pipe 5, is reduced by stopping the operation of the compressor 4or the like so that the forward drive force F1 is equal to or less thanthe force F2+Fs−Ff, thereby the piston cylinder 12 moves from the secondposition to the first position as shown in FIG. 24.

When the piston cylinder 12 is moved from the second position to thefirst position, the energizing force due to the coil spring 29 k affectsthe selector valve element 29 e, which has been in its action by the pin29 f, then the state-holding selector valve 29 is changed to be in thefirst state in which the pressure-transducing chamber R₂ communicateswith the channel 14A from the second state in which thepressure-transducing chamber R₂ communicates with the channel 14B.

Therefore, when the refrigerating cycle A is operated in the heatingmode, the refrigerant pressure, at the position situated between theelectrically-driven expansion valve 10A and the capillary tube 10B inthe refrigerating cycle A, is set high by controlling theelectrically-driven expansion valve 10A into its closed side uponstarting of operation of the compressor 4 so that the resultant forceF2+Fs+Ff is equal to or more than the forward drive force F1, therebythe piston cylinder 12 is kept staying at the first position.

On the other hand, when the refrigerating cycle A is operated in thecooling mode, the refrigerant pressure, at the position situated betweenthe electrically-driven expansion valve 10A and the capillary tube 10Bin the refrigerating cycle A, is set low by controlling theelectrically-driven expansion valve 10A into its open side upon startingof operation of the compressor 4 so that the resultant force F2+Fs+Ff isless than the forward drive force F1, thereby the piston cylinder 12 ismoved from the first position to the second position right after theoperation of the compressor 4.

Then, once the piston cylinder 12 is moved to the second position, aslong as the forward drive force F1 is greater than the force F2+Fs−Ff,the piston cylinder 12 is kept staying at the second position even ifthe opening ratio of the electrically-driven expansion valve 10A isthrottled, thereby the piston cylinder 12 is kept staying at the secondposition and the refrigerating cycle A is kept being operated in thecooling mode.

Thus, in the ninth embodiment, there is provided the state-holdingselector valve 29, by which the pressure-transducing chamber R₂ of thereversing valve housing 1 is selectively connected to either theposition situated between the electrically-driven expansion valve 10Aand the capillary tube 10B in the refrigerating cycle A or the inletpipe 6 through the channel 14A or 14B.

Therefore, the heating mode, in which the refrigerant discharged fromthe compressor 4 is supplied to the indoor heat exchanger 9A by way ofthe pipe 7, and the cooling mode, in which the refrigerant dischargedfrom the compressor 4 is supplied to the outdoor heat exchanger 9B byway of the pipe 8, can be selected by a change in the pressure of thedischarged refrigerant or by a change in the pressure of the refrigerantat the position situated between the electrically-driven expansion valve10A and the capillary tube 10B upon start of operation of the compressor4 and the selected state can be maintained, without using any exclusivepower source such as an electromagnetic solenoid.

According to the ninth embodiment, since a power for the selectionoperation of the channel selector valve is obtained from a change in therefrigerant pressure in the high pressure chamber R₁ of the reversingvalve housing 1 and in the pressure-transducing chamber R₂ bycontrolling the open ratio of the electrically-driven expansion valve10A, there is no necessity of using an electrically-driven drive sourcesuch as an electromagnetic solenoid, which has been explained in theprior art section of the present specification.

In the following, a channel selector valve, in which the channel isselected by a change in a oscillational frequency generated by acompressor, according to a tenth embodiment of the present inventionwill be explained with reference to FIGS. 28 and 29.

FIG. 28 is a view illustrating a schematic constitution of arefrigerating cycle employing the channel selector valve according tothe tenth embodiment of the present invention, in which the sameabbreviation numerals with those used for the corresponding identicalmembers or parts of the refrigerating cycle according to the ninthembodiment shown in FIG. 24 are used.

As shown in FIG. 28, the channel selector valve according to the tenthembodiment is different from the channel selector valve according to theninth embodiment shown in FIG. 24 in points that a state-holdingselector valve 29A without the first port 29 b (of the state-holdingselector valve 29) is employed instead of the state-holding selectorvalve 29, that a channel 14C diverged from the channel 14B is connectedto the pressure-transducing chamber R₂ through the stopper 3 from theoutside of the reversing valve housing 1, and that a pilot oscillationvalve 30 is provided in the channel 14C.

As shown in FIG. 29, the pilot oscillation valve 30 comprises a housing30 a, an oscillator 30 d received in the housing 30 a, a ball valve 30 freceived in the oscillator 30 d, and coil springs 30 g, 30 h and 30 j.

A first port 30 b, which communicates the interior of thepressure-transducing chamber R₂ to the interior of the housing 30 a, isformed at one end surface of the housing 30 a, while a second port 30 ccommunicating with the channel 14B is formed at an opposite end surfaceof the housing 30 a.

The oscillator 30 d has a flange 30 e at the center in the lengthdirection of its cross section and the coil springs 30 g and 30 h areprovided at both sides of the oscillator 30 d in the length direction ofits cross section, wherein the coil spring 30 g is provided between theflange 30 e and the one end surface of the housing 30 a, while the coilspring 30 h is provided between the flange 30 e and the opposite endsurface of the housing 30 a.

The coil springs 30 j are provided between the flange 30 e and an innerwall of the housing 30 a with leaving a space in the circumferentialdirection of the housing 30 a, while the ball valve 30 f is partiallyburied in an end surface of the oscillator 30 d, said end surface beingsituated at the opposite end surface of the housing 30 a.

The oscillator 30 d is movable in directions of three dimensions by thecoil springs 30 g, 30 h and 30 j and supported by elastic forces of thecoil springs 30 g, 30 h and 30 j so as to come back to a standardposition where the ball valve 30 f closes the second port 30 c.

According to the pilot oscillation valve 30 constructed as mentionedabove, when an oscillation having a specific frequency is generated inthe housing 30 a, the oscillator 30 d resonates because a balance amongthe elastic forces of the coil springs 30 g, 30 h and 30 j is lost,thereby the oscillator 30 d periodically moves on a specificthree-dimensional locus and the ball valve 30 f opens the second port 30c.

On the other hand, according to the pilot oscillation valve 30, when anoscillation having a different frequency from the specific frequency isgenerated in the housing 30 a or when no oscillation takes place in thehousing 30 a, the oscillator 30 d is situated at the standard positionby the elastic forces of the coil springs 30 g, 30 h and 30 j so thatthe ball valve 30 f keeps closing the second port 30 c.

In the following, an operation of the channel selector valve accordingto the tenth embodiment constructed as described above will beexplained.

When the operation of the compressor 4 is halted, as shown in FIG. 28,the piston cylinder 12 is situated at the first position, the inlet pipe6 communicates with the pipe 8 while the outlet pipe 5 communicates withthe pipe 7, then in this situation the oscillator 30 d of the pilotoscillation valve 30 is situated at the standard position and the ballvalve 30 f closes the second port 30 c.

Then, when the compressor 4 starts to operate, an oscillation of thecompressor 4 is propagated to the reversing valve housing 1, the stopper3 and the housing 30 a through the inlet valve 6 and the channel 14C,thereby the housing 30 a oscillates with a frequency corresponding tothe oscillation of the compressor 4.

If the oscillation of the housing 30 a has not the specific frequency,the oscillator 30 d is situated at the standard position and the ballvalve 30 f closes the second port 30 c, that is, thepressure-transducing chamber R₂ is isolated from the inlet pipe 6,therefore, the piston cylinder 12 is kept staying at the first positionas long as the forward drive force F1 is equal to or less than theresultant force F2+Fs+Ff.

If the piston cylinder 12 is kept staying at the first position, theselector valve element 29 e is kept energized by the coil spring 29 k,therefore, the state-holding selector valve 29 keeps staying in thefirst state, in which the pressure-transducing chamber R₂ is isolatedfrom the channel 14B and the refrigerant pressure in thepressure-transducing chamber R₂ does not change, thereby the pistoncylinder 12 keeps staying at the first position.

On the contrary, if the oscillation of the housing 30 a has the specificfrequency, the oscillator 30 d resonates and the ball valve 30 f opensthe second port 30 c, then the pressure-transducing chamber R₂communicates with the inlet pipe 6 of the compressor 4 through the pilotoscillation valve 30 and the channel 14C, thereby the refrigerantpressure in the pressure-transducing chamber R₂ becomes equal to therefrigerant pressure in the inlet pipe 6, which is much lower than thepressure of the refrigerant flowed into the high pressure space S2.

Therefore, the forward drive force F1 exceeds the resultant forceF2+Fs+Ff, as a result, the piston cylinder 12 moves from the firstposition to the second position.

When the piston cylinder 12 moves from the first position to the secondposition, the pin 29 f, which is pushed toward the closed end of thehousing 29 a by the piston cylinder, makes the selector valve element 29e be in selecting operation against the energizing force due to the coilspring 29 k, then the state-holding selector valve 29 changes its statefrom the first state to the second state so as to communicate thepressure-transducing chamber R₂ to the channel 14B, that is, thepressure-transducing chamber R₂ communicates with the inlet pipe 6through a different path from the path of the pilot oscillation valve 30and the channel 14C.

Therefore, thereafter, even if the oscillation of the compressor 4changes, that is, the oscillation frequency of the housing 30 a ischanged from the specific frequency and the oscillator 30 d comes backto the standard position and then the ball valve 30 f closes the secondport 30 c, the refrigerant pressure in the pressure-transducing chamberR₂ is kept equal to the refrigerant pressure in the inlet pipe 6,thereby the piston cylinder 12 keeps staying at the second position.

Further, thereafter, if the pressure of the refrigerant flowed into thehigh pressure space S2 from the compressor 4 through the outlet pipe 5is reduced by tentatively halting the operation of the compressor 4 andthe like so as to move the piston cylinder 12 from the second positionto the first position, the state-holding selector valve 29 changes itsstate from the second state to the first state by the energizing forcedue to the coil spring 29 k, said energizing force affecting theselector valve element 29 e that has been made be in selecting operationby the pin 29 f, thereby the oscillator 30 d comes back to the standardposition and the ball valve 30 f keeps closing the second port 30 c.

Consequently, when the refrigerating cycle A is operated in the heatingmode, the number of revolution of the compressor 4 upon start of itsoperation is set so that the housing 30 a oscillates with a frequency,which is different from the specific frequency, by the oscillation ofthe compressor 4 propagated through the reversing valve housing 1,stopper 3, the inlet pipe 6 and the channel 14C, thereby the pistoncylinder 12 can be kept staying at the first position.

On the other hand, when the refrigerating cycle A is operated in thecooling mode, the number of revolution of the compressor 4 upon start ofits operation is set so that the housing 30 a oscillates with thespecific frequency by the oscillation of the compressor 4 propagatedthrough the reversing valve housing 1, stopper 3, the inlet pipe 6 andthe channel 14C, thereby the piston cylinder 12 can be moved from thefirst position to the second position right after the operation of thecompressor 4.

Then, once the piston cylinder 12 is moved to the second position, aslong as the compressor 4 keeps operating, the piston cylinder 12 is keptstaying at the second position even if the oscillation of the compressor4 changes and the oscillation frequency of the housing 30 a changes fromthe specific frequency, thereby the refrigerating cycle A is keptoperating in the cooling mode.

The channel selector valve according to the tenth embodiment constructedas described above gives a similar effect with that according to theninth embodiment.

According to the tenth embodiment, since a power for the selectionoperation of the channel selector valve is obtained from a change in therefrigerant pressure in the high pressure chamber R₁ of the reversingvalve housing 1 and in the pressure-transducing chamber R₂ by the pilotoscillation valve 30, in which the pilot oscillation valve 30 opens orcloses depending upon a change in the frequency of the oscillationgenerated by the compressor 4, therefore similarly to the ninthembodiment, there is no necessity of using an electrically-driven drivesource such as an electromagnetic solenoid, which has been explained inthe prior art section of the present specification.

In addition, according to the tenth embodiment, upon starting of theoperation of the compressor 4 there is no necessity of adjusting thepressure of the refrigerant, which is introduced into thepressure-transducing chamber R₂ through the channel 14A by opening orclosing of the electrically-driven expansion valve 10A in therefrigerating cycle A, said adjusting is needed in the ninth embodiment,therefore, the constitution of the channel selector valve according tothe tenth embodiment becomes simple since there is noelectrically-driven expansion valve 10A needed in the refrigeratingcycle A, thereby the selector operation of the channel selector valvefor selecting the heating and cooling modes can be more easilyperformed.

In the ninth and tenth embodiments, the piston cylinder 12 may beprovided with a pin instead of providing the selector valve element 29 ewith the pin 29 f.

In the following, a channel selector valve, in which the channel isselected by adjusting a heat-exchange capacity by heat exchangers,according to a eleventh embodiment of the present invention will beexplained with reference to FIGS. 30 and 31.

FIG. 30 is a view illustrating a schematic constitution of arefrigerating cycle employing the channel selector valve according tothe eleventh embodiment of the present invention, in which the sameabbreviation numerals with those used for the corresponding identicalmembers or parts of the refrigerating cycle according to the ninthembodiment shown in FIG. 24 are used.

As shown in FIG. 30, the channel selector valve according to theeleventh embodiment is different from the channel selector valveaccording to the ninth embodiment shown in FIG. 24 in points that theelectrically-driven expansion valve 10A is omitted and that adifferential pressure selector valve 40 is provided between the outletpipe 5 and the inlet pipe 6.

As shown in FIG. 31, the differential pressure selector valve 40comprises the housing 40 a, a bellows 40 b received in the housing 40 a,a valve element 40 f for opening or closing a valve port 40 e thatpartitions the housing 40 a into a first chamber 40 c and a secondchamber 40 d by expansion and contraction of the bellows 40 b, and apilot valve 40 h, which opens or closes a pilot path 40 g that passesthrough the valve element 40 f and communicates with the interior of thebellows 40 b, by opening and closing action of the valve element 40 f,wherein the bellows 40 b is energized by a coil spring 40 j in adirection of expansion and contraction of the bellows 40 b, and thevalve element 40 f is energized toward a direction of closing the valveport 40 e by the energized force.

The first chamber 40 c is connected to the channel 14A, the secondchamber 40 d communicates with the inlet pipe 6 through the channel 14D,and the interior of the bellows 40 b communicates with the outlet pipe 5through the channel 14E.

In the following, an operation of the channel selector valve accordingto the eleventh embodiment will be explained. The bellows 40 b, intowhich the refrigerant is introduced from the outlet pipe 5 through thechannel 14E, keeps its contracted state as long as a differentialpressure between the refrigerant in the bellows 40 b and the refrigerantin the second chamber 40 d, which is introduced from the inlet pipe 6through the channel 14D, is equal to or lower than the energizing forceby the coil spring 40 j, then the valve element 40 f keeps closing thevalve port 40 e, on the other hand, when said differential pressureexceeds the energizing force by the coil spring 40 j, the bellows 40 bexpands and the valve element 40 f opens the valve port 40 e.

Here, if a differential pressure of the refrigerant, which exceeds theenergizing force by the coil spring 40 j, is defined as a differentialpressure threshold Pk, Pk is determined from a relation with theenergizing force by the coil spring 40 j, however usually, thedifferential pressure of the refrigerant is not set to be Pk, that is, ausual differential pressure of the refrigerant is kept to be lower thanthe energizing force by the coil spring 40 j.

When the refrigerating cycle A is operated in the heating mode, thedifferential pressure of the refrigerant is controlled to be lower thanthe energizing force by the coil spring 40 j, thereby the valve element40 f closes the valve port 40 e and the refrigerant discharged from thecompressor 4 is introduced into the pressure-transducing chamber R₂through the outlet pipe 5, the channel 14E, the interior of the bellows40 b, the pilot path 40 g of the valve element 40 f, and the channel14A, thereby the refrigerant pressure in the high pressure chamber R₁ ismade to be equal to the refrigerant pressure in the pressure-transducingchamber R₂, therefore the piston cylinder 12 is made situated at thefirst position.

On the other hand, when the refrigerating cycle A is operated in thecooling mode, the differential pressure of the refrigerant is oncecontrolled to be Pk that is higher than the energizing force by the coilspring 40 j, thereby the valve element 40 f opens the valve port 40 edue to the expansion of the bellows 40 b and the pilot valve 40 h closesthe pilot path 40 g, then the pressure-transducing chamber R₂communicates with the inlet pipe 6 through the channel 14A, the valveport 40 e, the channel 14D and then, the refrigerant pressure in thepressure-transducing chamber R₂ is made lower than the refrigerantpressure in the high pressure chamber R₁, thereby the piston cylinder 12is moved from the first position to the second position.

Once the piston cylinder 12 is moved to the second position, thereafter,the piston cylinder 12 is kept staying at the second position by thestate-holding selector valve 29, therefore the cooling mode ismaintained even if the refrigerant pressure is controlled to be lowerthan the energizing force by the coil spring 40 j.

In order to control the refrigerant pressure to be the differentialpressure threshold Pk, the easiest method is to change a heat-exchangecapacity of the indoor heat exchanger 9A and the outdoor heat exchanger9B. For example, if an operation of an air blower of the indoor heatexchanger 9A or the outdoor heat exchanger 9B is halted, the thermalconduction therein is impeded and the efficiency of heat exchange isdecreased, as a result, the refrigerant pressure increases while thepressure of the refrigerant sucked into the compressor 4 is lowered,thereby the differential pressure of the refrigerant is easily made tobe Pk.

The channel selector valve according to the eleventh embodimentconstructed as described above gives a similar effect with thataccording to the ninth or tenth embodiment.

According to the eleventh embodiment, since a power for the selectionoperation of the channel selector valve is obtained by changing thedifferential pressure between the refrigerant in the high pressurechamber R₁ of the reversing valve housing 1 and the refrigerant in thepressure-transducing chamber R₂, due to the change in the refrigerantpressure generated by the change in the efficiency of heat exchange inthe indoor heat exchanger 9A or the outdoor heat exchanger 9B,therefore, similarly to the channel selector valve according to theninth or tenth embodiment, there is no necessity of using anelectrically-driven drive source such as an electromagnetic solenoid,which has been explained in the prior art section of the presentspecification.

In the following, a channel selector valve according to a twelfthembodiment of the present invention, in which a selection operation isperformed by two three-way selector valves, will be explained withreference to FIG. 32.

FIG. 32 is a view illustrating a schematic constitution of arefrigerating cycle employing a channel selector valve according to thetwelfth embodiment of the present invention, in which the sameabbreviation numerals with those used for the corresponding identicalmembers or parts of the channel selector valve according to the firstembodiment shown in FIG. 1 are used.

The channel selector valve according to the twelfth embodiment, a statein operation in the hearting mode of which is shown in FIG. 32 by itssectional view, is different from the channel selector valve accordingto the first embodiment shown in FIG. 1 in points that a four-wayselector valve is constituted by two three-way selector valves, i.e. afirst three-way selector valve 41 and a second three-way selector valve42, which are connected in parallel to a series circuit comprising anindoor heat exchanger 9A, a throttle 10 and an outdoor heat exchanger 9Band that the two three-way selector valves, i.e. a first three-wayselector valve 41 and a second three-way selector valve 42 are connectedto a compressor 4.

As shown in FIG. 32, the first three-way selector valve 41 comprises areversing valve housing 1 (corresponding to a housing), an outlet pipe5, pipe 7A and pipe 7B, which are connected to the reversing valvehousing 1, and a piston 41 a (corresponding to a movable member) thatallows the outlet pipe 5 to communicate with either the pipe 7A or thepipe 7B through the interior of the reversing valve housing 1.

The reversing valve housing 1 of the first three-way selector valve 41has a cylindrical shape, in which a large diameter cylinder 1 a issandwiched by two small diameter cylinders 1 b and 1 c, wherein thepipes 7A and 7B are connected to the small diameter cylinder 1 b and 1c, respectively, and the outlet pipe 5 is connected to the largediameter cylinder 1 a.

In the interior of the small diameter cylinders 1 b and 1 c, there areprovided bearings 41 b and 41 c, respectively, by which a slide shaft 41d is supported rotatively and slidably in an axial direction, inaddition, there are provided channels 41 e and 41 f passing throughbetween each end of the bearings 41 b and 41 c, respectively.

On a circumferential surface of the slide shaft 41 d, there are putstoppers 41 g and 41 h (for example, E-rings) in the axial directionwith leaving a space therebetween, then a coil spring 41 j(corresponding to second storing means for storing energizing force) isprovided between the stoppers 41 g and the bearing 41 b, while a coilspring 41 k (corresponding to first storing means for storing energizingforce) is provided between the stoppers 41 h and the bearing 41 c, saidcoil springs 41 j and 41 k being put on the slide shaft 41 d.

The piston 41 a is formed to have a diameter, which is larger than thatof the small diameter cylinders 1 b and 1 c but smaller than that of thelarge diameter cylinder la, and is received in the large diametercylinder 1 a. The piston 41 a is put on the slide shaft 41 d so as to beslidable in the axial direction of the slide shaft 41 d between thestopper 41 g and the stopper 41 h, then there is provided an O-ring 41 mfor sealing between the piston 41 a and the slide shaft 41 d.

The outlet pipe 5 is connected to an outlet (not shown in the figure) ofthe compressor 4, the pipe 7A is connected to the indoor heat exchanger9A while the pipe 8A is connected to the outdoor heat exchanger 9B.

In the first three-way selector valve 41 thus formed, when a forcelarger than an elastic force of the coil spring 41 k is applied on anend surface of the slide shaft 41 d at the small diameter cylinder 1 bside, the slide shaft 41 d moves toward the small diameter cylinder 1 cside.

Then, the piston 41 a moves to the first position where the piston 41 apushed by the stopper 41 g closes a valve port 1 e, which is formed by alevel difference between the large diameter cylinder 1 a and the smalldiameter cylinder 1 c, and opens a valve port 1 d, which is formed by alevel difference between the large diameter cylinder 1 a and the smalldiameter cylinder 1 b, thereby the outlet pipe 5 communicates with thepipe 7A through the channel 41 e of the bearing 41 b.

When the piston 41 a is at the first position, the coil spring 41 k ispressed by the stopper 41 h to be compressed, thereby the coil spring 41k is in a state that the coil spring 41 k stores an energized force tomove the slide shaft 41 d toward the small diameter cylinder 1 b side.

Then, in a state shown in FIG. 32, if a force applied on the end surfaceof the slide shaft 41 d at the small diameter cylinder 1 b side isremoved, the stopper 41 h is pushed by the elastic force of the coilspring 41 k so that the slide shaft 41 d moves toward the small diametercylinder 1 b side.

Then, by a sliding resistance between the O-ring 41 m and the slideshaft 41 d, the piston 41 a together with the slide shaft 41 d moves tothe second position where the piston 41 a opens the valve port 1 e andcloses the valve port 1 d, thereby the outlet pipe 5 communicates withthe pipe 8A through the channel 41 f of the bearing 41 c.

However, in a state that the slide shaft 41 d merely moves toward thesmall diameter cylinder 1 b side by the elastic force of the coil spring41 k, the piston 41 a does not move with relation to the slide shaft 41d, therefore, the piston 41 a abuts on the stopper 41 g and is apartfrom the stopper 41 h, while the coil spring 41 j extends.

Then, when a force larger than the elastic force of the coil spring 41 jis applied on an end surface of the slide shaft 41 d at the smalldiameter cylinder 1 c side, only the slide shaft 41 d moves toward thesmall diameter cylinder 1 b side until the stopper 41 h abuts on thepiston 41 a, thereby the stopper 41 g is apart from the piston 41 atoward the small diameter cylinder 1 b side.

Then, the coil spring 41 j is pressed by the stopper 41 g to becompressed, thereby the coil spring 41 j is in a state that the coilspring 41 j stores an energized force to move the slide shaft 41 dtoward the small diameter cylinder 1 c side.

Then, in this state, if a force applied on the end surface of the slideshaft 41 d at the small diameter cylinder 1 c side is removed, the slideshaft 41 d moves toward the small diameter cylinder 1 c side by theelastic force of the coil spring 41 j.

Then, by a sliding resistance between the O-ring 41 m and the slideshaft 41 d, the piston 41 a together with the slide shaft 41 d moves tothe first position where the piston 41 a closes the valve port 1 e andopens the valve port 1 d, thereby the outlet pipe 5 communicates withthe pipe 7A through the channel 41 e of the bearing 41 b.

However, in a state t hat the slide shaft 41 d merely moves toward thesmall diameter cylinder 1 c side by the elastic force of the coil spring41 j, the piston 41 a does not move with relation to the slide shaft 41d, therefore, the piston 41 a abuts on the stopper 41 h and is apartfrom the stopper 41 g, while the coil spring 41 k extends.

Then, when a force larger than the elastic force of the coil spring 41 kis applied on an end surface of t he slide shaft 41 d at the smalldiameter cylinder 1 b side, only the slide shaft 41 d moves toward thesmall diameter cylinder 1 c side until the stopper 41 g abuts on thepiston 41 a, thereby the stopper 41 h is apart from the piston 41 atoward the small diameter cylinder 1 c side.

Then, the coil spring 41 k is pressed b y the stopper 41 g to becompressed, thereby the coil spring 41 k comes back to the state shownin FIG. 32, in which the coil spring 41 k stores an energized force tomove the slide shaft 41 d toward the small diameter cylinder 1 b side.

On the other hand, the second three-way selector valve 42 comprises areversing valve housing 1 (corresponding to a housing), an inlet pipe 6,pipe 7B and pipe 8B, which are connected to the reversing valve housing1, and two pistons 42 a and 42 b (corresponding to a movable member)that allows the inlet pipe 6 to communicate with either the pipe 7B orthe pipe 8B through the interior of the reversing valve housing 1.

The reversing valve housing 1 of the second three-way selector valve 42has a cylindrical shape, in which a small diameter cylinder 1 f issandwiched by two large diameter cylinders 1 g and 1 h, wherein thepipes 7B and 8B are connected to the small diameter cylinder 1 g and 1h, respectively, and the inlet pipe 6 is connected to the small diametercylinder 1 f.

In the reversing valve housing 1, there is provided a slide shaft 42 cmovable in a thrust direction, on which stoppers 42 d, 42 e, 42 f and 42g (for example, E-rings) are put in the axial direction with leaving aspace therebetween.

Each piston 42 a and 42 b is formed to have a diameter, which is largerthan that of the small diameter cylinder 1 f but smaller than that ofthe large diameter cylinders 1 g and 1 h, the pistons 42 a and 42 b arereceived in the large diameter cylinders 1 g and 1 h, respectively. Thepiston 42 a is put on the slide shaft 42 c so as to be slidable in theaxial direction of the slide shaft 42 c between the stopper 42 d and thestopper 42 e, while the piston 42 b is put on the slide shaft 42 c so asto be slidable in the axial direction of the slide shaft 42 c betweenthe stopper 42 f and the stopper 42 g.

In the large diameter cylinder 1 g, there is received a coil spring 42 hfor energizing the piston 42 a toward the large diameter cylinder 1 hside, while in the large diameter cylinder 1 h, there is received a coilspring 42 j for energizing the piston 42 b toward the large diametercylinder 1 g side, wherein there are provided O-rings 42 k and 42 m forsealing between each piston 42 a and 42 b and the slide shaft 42 c.

The inlet pipe 6 is connected to a inlet (not shown in the figure) ofthe compressor 4, the pipe 7B is connected to the indoor heat exchanger9A and the pipe 7A of the first three-way selector valve 41, while thepipe 8B is connected to the outdoor heat exchanger 9B and the pipe 8A ofthe first three-way selector valve 41.

In the second three-way selector valve 42 constructed as describedabove, when a force stronger than an elastic force by the coil spring 42j is applied to the slide shaft 42 c from the large diameter cylinder 1g side, the slide shaft 42 c pushed by the stopper 42 d slides towardthe large diameter cylinder 1 h side.

Then, the piston 42 b pushed by the stopper 42 f moves to the secondposition where the piston 42 b opens a valve port 1 m formed by a leveldifference between the small diameter cylinder 1 f and the largediameter cylinder 1 h, while the piston 42 a moves to the secondposition where the piston 42 a closes a valve port 1 k formed by a leveldifference between the small diameter cylinder 1 f and the largediameter cylinder 1 g by a sliding resistance between the O-ring 42 kand the slide shaft 42 c, thereby the inlet pipe 6 is communicated tothe pipe 8B.

Then, at the second position of the piston 42 a, the coil spring 42 j ispressed by the piston 42 b to be compressed, thereby the coil spring 42j is in a state that the coil spring 42 j stores an energized force tomove the piston 42 b toward the large diameter cylinder 1 g side.

Then, in the second three-way selector valve 42, in the state shown inFIG. 32, if a force applied to the slide shaft 42 c from the largediameter cylinder 1 g side is removed, the piston 42 b is pressed by theelastic force of the coil spring 42 j and moves toward the firstposition where the piston 42 b closes the valve port 1 m, that is, theslide shaft 42 c moves toward the large diameter cylinder 1 g side.

Then, until the slide shaft 42 c is on a half way of moving toward thelarge diameter cylinder 1 g side, due to the sliding resistance betweenthe O-ring 42 k and the slide shaft 42 c, the piston 42 a together withthe slide shaft 42 c moves to the first position where the piston 42 aopens the valve port 1 k, thereby the inlet pipe 6 is communicated tothe pipe 7B.

Then, in this state, if the slide shaft 42 c moves further toward thelarge diameter cylinder 1 g side, an elastic force stronger than thesliding resistance between the O-ring 42 k and the slide shaft 42 c actsfrom the coil spring 42 h to the piston 42 a. Due to this elastic force,the piston 42 a stops at the first position, while only the slide shaft42 c moves toward the large diameter cylinder 1 g side, then the stopper42 d that has abutted on the piston 42 a is away from the piston 42 a,while the stopper 42 e that has been away from the piston 42 a comes incontact with the piston 42 a.

In this state, if a force stronger than the elastic force by the coilspring 42 h is applied from the large diameter cylinder 1 h side to theslide shaft 42 c, the piston 42 a is pressed by the stopper 42 e to movetoward the large diameter cylinder 1 g side, thereby the coil spring 42h is pressed by the piston 42 a to be compressed and the coil spring 42h is in a state that the coil spring 42 h stores the energizing force tomove the piston 42 a toward the large diameter cylinder 1 h side.

At the same time, since at the first position where the piston 42 bcloses the valve port 1 m the piston 42 b is controlled from movingfurther toward the large diameter cylinder 1 g side, the stopper 42 fthat has abutted on the piston 42 b is away from the piston 42 b, whilethe stopper 42 g that has been away from the piston 42 b comes incontact with the piston 42 b.

In this state, if the force applied from the large diameter cylinder 1 hside to the slide shaft 42 c is removed, the piston 42 a is pressed bythe elastic force of the coil spring 42 h, thereby the piston 42 a movesto the second position where the piston 42 a closes the valve port 1 kand the slide shaft 42 c moves toward the large diameter cylinder 1 hside.

Then, until the slide shaft 42 c is on a half way of moving toward thelarge diameter cylinder 1 h side, due to the sliding resistance betweenthe O-ring 42 m and the slide shaft 42 c, the piston 42 b together withthe slide shaft 42 c moves to the second position where the piston 42 bopens the valve port 1 m, thereby the inlet pipe 6 is communicated tothe pipe 8B.

Then, in this state, if the slide shaft 42 c moves further toward thelarge diameter cylinder 1 h side, an elastic force stronger than thesliding resistance between the O-ring 42 m and the slide shaft 42 c actsfrom the coil spring 42 j to the piston 42 b. Due to this elastic force,the piston 42 b stops at the second position, while only the slide shaft42 c moves toward the large diameter cylinder 1 h side, then the stopper42 g that has abutted on the piston 42 b is away from the piston 42 b,while the stopper 42 f that has been away from the piston 42 b comes incontact with the piston 42 b.

In this state, if a force stronger than the elastic force by the coilspring 42 j is applied from the large diameter cylinder 1 g side to theslide shaft 42 c, the piston 42 b is pressed by the stopper 42 f to movetoward the large diameter cylinder 1 h side, thereby the coil spring 42j is pressed by the piston 42 b to be compressed and the coil spring 42j is in a state that the coil spring 42 j stores the energizing force tomove the piston 42 b toward the large diameter cylinder 1 g side.

At the same time, since at the second position where the piston 42 acloses the valve port 1 k the piston 42 a is controlled from movingfurther toward the large diameter cylinder 1 h side, the stopper 42 ethat has abutted on the piston 42 a is away from the piston 42 a, whilethe stopper 42 d that has been away from the piston 42 a comes incontact with the piston 42 a, thereby coming back to the state shown inFIG. 32.

In the following, an operation of the channel selector valve accordingto the twelfth embodiment constructed as described above will beexplained.

When the operation of the compressor 4 is halted, the coil springs 41 jand 41 k of the first three-way selector valve 41 as well as the coilsprings 42 h and 42 j of the second three-way selector valve 42 are allextended and are in a state to have no energizing force, that is, thepiston 41 a of the first three-way selector valve 41 and the piston 42 aof the second three-way selector valve 42 are located at each samepositions with those during an ex-operation of the compressor 4.

In a state that the piston 41 a of the first three-way selector valve 41is at the first position and the pistons 42 a and 42 b of the secondthree-way selector valve 42 are at their second position, when thecompressor 4 starts to operate, a high pressure refrigerant dischargedfrom the compressor 4 flows into the large diameter cylinder 1 a of thefirst three-way selector valve 41 through the outlet pipe 5 and then,further flows into the indoor heat exchanger 9A through the valve port 1d, the channel 41 e of the bearing 41 b and the pipe 7A.

Then, the refrigerant flowed into the indoor heat exchanger 9A flowsinto the pipe 8B of the second three-way selector valve 42 by way of thethrottle 10, the outdoor heat exchanger 9B, and then, flows back to theinlet of the compressor 4 by way of the valve port 1 m and the inletpipe 6, thereby the refrigerating cycle A is in the heating mode.

At this time, in the first three-way selector valve 41, since therefrigerant pressure in the pipe 7A communicating with the outlet of thecompressor 4 is higher than that in the pipe 8A communicating with theinlet of the compressor 4 through the second three-way selector valve42, the slide shaft 41 d is pressed toward the small diameter cylinder 1c side by a force stronger than the elastic force of the coil spring 41k causing the coil spring 41 k to be compressed, thereby the coil spring41 k stores the energizing force to energize the slide shaft 41 d towardthe small diameter cylinder 1 b side.

On the other hand, in the second three-way selector valve 42, since therefrigerant pressure in the pipe 7B communicating with the outlet of thecompressor 4 through the first three-way selector valve 41 is higherthan that in the pipe 8B communicating with the inlet of the compressor4, the slide shaft 42 c is applied by a force stronger than the elasticforce of the coil spring 42 j from the large diameter cylinder 1 g side,causing the piston 42 b to be pressed toward the large diameter cylinder1 h side and the coil spring 42 j to be compressed, thereby the coilspring 42 j stores the energizing force to energize the piston 42 btoward the large diameter cylinder 1 g side.

Thereafter, when the operation of the compressor 4 is halted, in thefirst three-way selector valve 41, the piston 41 a together with theslide shaft 41 d moves toward the small diameter cylinder 1 b side bythe energizing force stored in the coil spring 41 k, thereby the piston41 a is situated at the second position.

On the other hand, in the second three-way selector valve 42, by theenergizing force stored in the coil spring 42 j, the piston 42 b movestoward the large diameter cylinder 1 g side and is situated at the firstposition, while the slide shaft 42 c and the piston 42 a move togetherwith the piston 42 b, thereby the piston 42 a is situated at the firstposition.

In this state, when the compressor 4 starts to operate, a high pressurerefrigerant discharged from the compressor 4 flows into the largediameter cylinder 1 a of the first three-way selector valve 41 throughthe outlet pipe 5 and then, further flows into the outdoor heatexchanger 9B through the valve port 1 e, the channel 41 f of the bearing41 c and the pipe 8A.

Then, the refrigerant flowed into the outdoor heat exchanger 9B flowsinto the pipe 7B of the second three-way selector valve 42 by way of thethrottle 10, the indoor heat exchanger 9A, and then, flows back to theinlet of the compressor 4 by way of the valve port 1 k and the inletpipe 6, thereby the refrigerating cycle A is in the cooling mode.

At this time, in the first three-way selector valve 41, since therefrigerant pressure in the pipe 8A communicating with the outlet of thecompressor 4 is higher than that in the pipe 7A communicating with theinlet of the compressor 4 through the second three-way selector valve42, the slide shaft 41 d is pressed toward the small diameter cylinder 1b side by a force stronger than the elastic force of the coil spring 41j causing the coil spring 41 j to be compressed, thereby the coil spring41 j stores the energizing force to energize the slide shaft 41 d towardthe small diameter cylinder 1 c side.

On the other hand, in the second three-way selector valve 42, since therefrigerant pressure in the pipe 8B communicating with the outlet of thecompressor 4 through the first three-way selector valve 41 is higherthan that in the pipe 7B communicating with the inlet of the compressor4, the slide shaft 42 c is applied by a force stronger than the elasticforce of the coil spring 42 h from the large diameter cylinder 1 h side,causing the piston 42 a to be pressed toward the large diameter cylinder1 g side and the coil spring 42 h to be compressed, thereby the coilspring 42 h stores the energizing force to energize the piston 42 atoward the large diameter cylinder 1 h side.

Thereafter, when the operation of the compressor 4 is halted, in thefirst three-way selector valve 41, the piston 41 a together with theslide shaft 41 d moves toward the small diameter cylinder 1 c side bythe energizing force stored in the coil spring 41 j, thereby the piston41 a is situated at the first position.

On the other hand, in the second three-way selector valve 42, by theenergizing force stored in the coil spring 42 h, the piston 42 a movestoward the large diameter cylinder 1 h side and is situated at thesecond position, while the slide shaft 42 c and the piston 42 b movetogether with the piston 42 a, thereby the piston 42 b is situated atthe second position.

Thus, according to the twelfth embodiment, the four-way selector valve,which selects the channel of the refrigerant in the refrigerating cycleA, is constituted by the first three-way selector valve 41 and thesecond three-way selector valve 42, which select a path of therefrigerant upon halting of the operation of the compressor 4 by usingthe energizing force that is stored during the operation of thecompressor 4.

Therefore, the heating mode, in which the refrigerant discharged fromthe outlet pipe 5 is supplied to the indoor heat exchanger 9A by way ofthe pipe 7A of the first three-way selector valve 41, and the coolingmode, in which the refrigerant discharged from the outlet pipe 5 issupplied to the outdoor heat exchanger 9B by way of the pipe 8A of thefirst three-way selector valve 41, can be selected by controlling thenumber of times of the operation start of the compressor 4 and theselected state can be maintained without using any exclusive powersource such as an electromagnetic solenoid.

Moreover, according to the twelfth embodiment, since the selection ofcommunication for the outlet pipe 5 of the first three-way selectorvalve 41 and the inlet pipe 6 of the second three-way selector valve 42is performed according to a start and halt of the operation of thecompressor 4, neither power source for an electric drive nor control byan electric signal for selecting the channel of the refrigerant isneeded, therefore, the channel selector valve according to the twelfthembodiment is advantageous.

In the following, a channel selector valve according to a thirteenthembodiment of the present invention, in which a selection operation isperformed by a four-way selector valve that uses a three-way selectorvalve as a pilot valve thereof, will be explained with reference to FIG.33.

FIG. 33 is a view illustrating a schematic constitution of arefrigerating cycle A employing the channel selector valve according tothe thirteenth embodiment of the present invention, in which the sameabbreviation numerals with those used for the corresponding identicalmembers or parts of the channel selector valve according to the thirdembodiment shown in FIG. 6 are used.

The channel selector valve according to the thirteenth embodiment, anoperational state of which in the heating mode is shown by a sectionalview in FIG. 33, comprises a slide-type four-way selector valve 43 and athree-way selector valve (corresponding to the pilot valve) 44 thatfunctions as a pilot valve for the slide-type four-way selector valve43.

The slide-type four-way selector valve 43 is different from the channelselector valve according to the third embodiment shown in FIG. 6 inpoints that a second piston cylinder 12′ forming a secondpressure-transducing chamber (corresponding to the third pressurechamber) R₅, which faces a pressure-transducing chamber R₂ with puttinga high pressure chamber R₁ therebetween, is provided between a valveseat 11 and a stopper 2 in a reversing valve housing 1, that a secondconnecting shaft 28′ connects a slide valve 27 to the second pistoncylinder 12′, and that the compression spring 13, which energizes apiston cylinder 12 to move from the second position toward the firstposition, is omitted.

In the slide-type four-way selector valve 43, there are provided athrough hole (corresponding to the first equalizing path) 12 ₁′ in thepiston cylinder 12 and a second through hole (corresponding to thesecond equalizing path) 12 ₁′ in the second piston cylinder 12′. Thehigh-pressure chamber R₁ always communicates with the secondpressure-transducing chamber R₅ through the second through hole 12 ₁′.

One end of a channel 14F is connected to an inlet pipe 6 that isconnected to an inlet of the compressor 4, then a valve seat 2 a isformed on the stopper 2 to which one end of a channel 14G is connectedfrom the outside, while a valve seat 3 a is formed on a stopper 3 towhich one end of a channel 14H is connected from the outside.

In the piston cylinder 12, there is provided a subvalve (correspondingto the first subvalve) 12 ₂, which is apart from the valve seat 3 a ofthe stopper 3 when the piston cylinder 12 is at the first position asshown in FIG. 33 and communicates the channel 14H to thepressure-transducing chamber R₂, while in the second piston cylinder 12′there is provided a second subvalve 12 ₂′, which sits on the valve seat2 a of the stopper 2 when the piston cylinder 12 is at the firstposition as shown in FIG. 33 and makes the channel 14G insulated fromthe second pressure-transducing chamber R₅.

To the contrary, when the piston cylinder 12 is at the second position,that is, the inlet pipe 6 communicates with the pipe 7 through a closedspace S1 while the outlet pipe 5 communicates with the pipe 8 through ahigh pressure space S2, the subvalve 12 ₂ sits on the valve seat 3 a ofthe stopper 3 so as to make the channel 14H insulated from thepressure-transducing chamber R₂ while the second subvalve 12 ₂′ is apartfrom the valve seat 2 a of the stopper 2 so as to communicate thechannel 14G to the second pressure-transducing chamber R₅.

In the slide-type four-way selector valve 43, the piston cylinder 12 andthe second piston cylinder 12′ constitute the movable member describedin the claims.

The three-way selector valve 44 is provided outside of the slide-typefour-way selector valve 43 and comprises a housing (corresponding to thesecond housing) 44 a, to which each end of the channels 14F, 14G and 14His connected, and two pistons (corresponding to the selector valveelement) 44 b and 44 c, which make the channel 14F communicate witheither the channel 14G or the channel 14H by a selector operation.

The housing 44 a has a cylindrical shape, in which a small diametercylinder 1 f is sandwiched by two large diameter cylinders 1 g and 1 h,to which each opposite end of the channels 14H and 14G are connected,respectively, while the channel 14F is connected to the small diametercylinder 1 f.

In the housing 44 a, there is provided a slide shaft 44 d movable in athrust direction, on which stoppers 44 e, 44 f, 44 g and 44 h (forexample, E-rings) are put in the axial direction with leaving a spacetherebetween.

An outer diameter of each of pistons 44 b and 44 c is formed larger thanan inner diameter of the small diameter cylinder 1 f and smaller than aninner diameter of the large diameter cylinder 1 g and 1 h, the pistons44 b and 44 c are received in the large diameter cylinders 1 g and 1 h,respectively. The pistons 44 b and 44 c are attached to the slide shaft44 d so that the piston 44 b can slide in an axial direction of theslide shaft 44 d between the stoppers 44 e and 44 f, while the piston 44c can slide in an axial direction of the slide shaft 44 d between thestoppers 44 g and 44 h.

A coil spring 44 j, which energizes the slide shaft 44 d toward thelarge diameter cylinder 1 h side through the stopper 44 e, is receivedin the large diameter cylinder 1 g, while a coil spring 44 k, whichenergizes the slide shaft 44 d toward the large diameter cylinder 1 gside through the stopper 44 h, is received in the large diametercylinder 1 h. O-rings 44 m and 44 n for sealing are provided between theslide shaft 44 d and the pistons 44 b and 44 c, respectively.

In the large diameter cylinder 1 g, there is provided a ring-shapedstopper 44 p, an inner diameter of which is larger than an outerdiameter of the stopper 44 e and smaller than an outer diameter of thepiston 44 b, while in the large diameter cylinder 1 h, there is provideda ring-shaped stopper 44 r, an inner diameter of which is larger than anouter diameter of the stopper 44 h and smaller than an outer diameter ofthe piston 44 c.

As shown in FIG. 33, in the stopper 44 r there is provided a throughhole 44 t that allows the both sides of the stopper 44 r to communicatewith each other when the piston 44 c abuts on the stopper 44 r, likewisea the stopper 44 p is provided with a through hole 44 s.

In the three-way selector valve 44 thus constructed, when a forcestronger than an elastic force of the coil spring 44 k is applied to theslide shaft 44 d from the large diameter cylinder 1 g side, the slideshaft 44 d slides toward the large diameter cylinder 1 h side.

Then, the piston 44 c is pushed by the stopper 44 g to open a valve port1 m formed by a level difference between the small diameter cylinder 1 fand the large diameter cylinder 1 h and moves to the second positionwhere the piston 44 c abuts on the stopper 44 r, while the piston 44 bis pushed by the stopper 44 e to close a valve port 1 k formed by alevel difference between the small diameter cylinder 1 f and the largediameter cylinder 1 g and moves to the second position where the piston44 b is apart from the stopper 44 p, thereby the channel 14Fcommunicates with the channel 14G through the small diameter cylinder 1f, the large diameter cylinder 1 h and the through hole 44 t of thestopper 44 r.

When the piston 44 b is situated at the second position, the coil spring44 k is pressed by the stopper 44 h to be compressed, then the coilspring 44 k is in a state to store an energizing force to slide thestopper 44 h toward the large diameter cylinder 1 g side.

As to the three-way selector valve 44, in a state shown in FIG. 33, if aforce applied to the slide shaft 44 d from the large diameter cylinder 1g side is removed, the slide shaft 44 d is pushed by the elastic forceof the coil spring 44 k through the stopper 44 h to move toward thelarge diameter cylinder 1 g side, thereby the piston 44 c together withthe slide shaft 44 d closes the valve port 1 m by a sliding resistancebetween the O-ring 44 n and the slide shaft 44 d and moves to the firstposition where the piston 44 c is apart from the stopper 44 r.

While, by a sliding resistance between the O-ring 44 m and the slideshaft 44 d that moves toward the large diameter cylinder 1 g side, thepiston 44 b together with the slide shaft 44 d opens the valve port 1 kand moves to the first position where the piston 44 b abuts on thestopper 44 p, thereby the channel 14F communicates with the channel 14Hthrough the small diameter cylinder 1 f, the large diameter cylinder 1 gand the through hole 44 s of the stopper 44 p.

However, in a state that the slide shaft 44 d only has slided toward thelarge diameter cylinder 1 g side by the elastic force of the coil spring44 k, the pistons 44 b and 44 c do not move relatively with respect tothe slide shaft 44 d, therefore the piston 44 b abuts on the stopper 44e to be apart from the stopper 44 f while the piston 44 c abuts on thestopper 44 g to be apart from the stopper 44 h.

In this state, if a force stronger than the elastic force of the coilspring 44 j is applied to the slide shaft 44 d from the large diametercylinder 1 h side, the slide shaft 44 d further moves toward the largediameter cylinder 1 g side, thereby the coil spring 44 j is pressed bythe stopper 44 e to be compressed and is in a state to store theenergizing force to move the stopper 44 e toward the large diametercylinder 1 h side.

At this time, since the piston 44 c, situated at the first positionwhere the piston 44 c closes the valve port 1 m, is controlled to movefurther toward the large diameter cylinder 1 g side, the stopper 44 gthat has abutted on the piston 44 c is away from the piston 44 c, whilethe stopper 44 h that has been away from the piston 44 c abuts on thepiston 44 c.

Then, in this state, if a force applied to the slide shaft 44 d from thelarge diameter cylinder 1 h side is removed, the slide shaft 44 d ispushed by the elastic force of the coil spring 44 j through the stopper44 e to move toward the large diameter cylinder 1 h side, thereby thepiston 44 b together with the slide shaft 44 d closes the valve port 1 kby a sliding resistance between the O-ring 44 m and the slide shaft 44 dand moves to the second position where the piston 44 b is apart from thestopper 44 p.

While, by a sliding resistance between the O-ring 44 n and the slideshaft 44 d that moves toward the large diameter cylinder 1 h side, thepiston 44 c together with the slide shaft 44 d opens the valve port 1 mand moves to the second position where the piston 44 c abuts on thestopper 44 r, thereby the channel 14F communicates with the channel 14Gthrough the small diameter cylinder 1 f, the large diameter cylinder 1 hand the through hole 44 t of the stopper 44 r.

However, in a state that the slide shaft 44 d only has slided toward thelarge diameter cylinder 1 h side by the elastic force of the coil spring44 j, the pistons 44 b and 44 c do not move relatively with respect tothe slide shaft 44 d, therefore the piston 44 b abuts on the stopper 44f to be apart from the stopper 44 e while the piston 44 c abuts on thestopper 44 h to be apart from the stopper 44 g.

In this state, if a force stronger than the elastic force of the coilspring 44 k is applied to the slide shaft 44 d from the large diametercylinder 1 g side, the slide shaft 44 d further moves toward the largediameter cylinder 1 h side, thereby the coil spring 44 k is pressed bythe stopper 44 h to be compressed and is in a state to store theenergizing force to move the stopper 44 h toward the large diametercylinder 1 g side.

At this time, since the piston 44 b, situated at the second positionwhere the piston 44 b closes the valve port 1 k, is controlled to movefurther toward the large diameter cylinder 1 h side, the stopper 44 fthat has abutted on the piston 44 b is away from the piston 44 b, whilethe stopper 44 e that has been away from the piston 44 b abuts on thepiston 44 b, thereby coming back to the state shown in FIG. 33.

As to the slide-type four-way selector valve 43, a permanent magnet M isdisposed at an inner bottom of the second piston cylinder 12′, then ahall device H is disposed at an outer circumferential bottom of thereversing valve housing 1 near the pipe 8. When the piston cylinder 12and the piston cylinder 12′ (the movable member) are at the firstposition, a magnetic field due to the permanent magnet M is not detectedby the hall device H, on the other hand, when the piston cylinder 12 andthe piston cylinder 12′ are at the second position, a magnetic field dueto the permanent magnet M is detected by the hall device H. A signaldetected by the hall device H is inputted into a detecting element C3 ofa controller C (described later) in FIG. 62, by which it is detectedwhether the piston cylinder 12 and the second piston cylinder 12′ aresituated at the first position or the second position.

In the following, an operation of the channel selector valve accordingto the thirteenth embodiment constructed as described above will beexplained.

When the operation of the compressor 4 is halted, the piston cylinder 12and the second piston cylinder 12′ of the slide-type four-way selectorvalve 43 keep their positions during an ex-operation of the compressor4, while the pistons 44 b and 44 c have moved to the second position ifthey were at the first position during an ex-operation of the compressor4, on the other hand the pistons 44 b and 44 c have moved to the firstposition if they were at the second position during an ex-operation ofthe compressor 4.

As shown in FIG. 33, in a state that the refrigerating cycle A is in theheating mode, if the operation of the compressor 4 is halted, the pistoncylinder 12 of the slide-type four-way selector valve 43 does not moveand stays at the first position shown in FIG. 33, while the pistons 44 band 44 c of the three-way selector valve 44 move from the secondposition shown in FIG. 33 to the first position since the force appliedto the slide shaft 44 d from the large diameter cylinder 1 g is removed.

Therefore, the small diameter cylinder 1 f of the three-way selectorvalve 44, which communicates with the inlet pipe 6 through the channel14F, communicates with the large diameter cylinder 1 g through the valveport 1 k, which is opened by the piston 44 b situated at the firstposition, while the large diameter cylinder 1 g communicates with thepressure-transducing chamber R₂ of the slide-type four-way selectorvalve 43 through the valve seat 3 a that is opened by the subvalve 12 ₂and the channel 14H, thereby the inlet pipe 6 communicates with thepressure-transducing chamber R₂ through the three-way selector valve 44.

In this state, if the compressor 4 starts to operate, the high pressurerefrigerant discharged from the compressor 4 flows into the highpressure space S2 of the slide-type four-way selector valve 43 by way ofthe outlet pipe 5, then further flows into the indoor heat exchanger 9Athrough the pipe 7 and then, this refrigerant flows into the closedspace S1 through the throttle 10, the outdoor heat exchanger 9B and thepipe 8, then flows back to the inlet of the compressor 4 by way of theinlet pipe 6, thereby the refrigerating cycle A is in the heating mode.

At this time, since an amount of the refrigerant that can pass throughthe through hole 12 ₁ of the piston cylinder 12 is small, an incrementin the pressure of the refrigerant in the pressure-transducing chamberR₂ of the slide-type four-way selector valve 43 upon starting of theoperation of the compressor 4 is small, therefore a difference in thepressure between the refrigerant in the pressure-transducing chamber R₂communicating with the inlet pipe 6 through the three-way selector valve44 and the refrigerant in the high pressure space S2 becomes large.

Therefore, the piston cylinder 12 and the second piston cylinder 12′ ofthe slide-type four-way selector valve 43 move from the first positionshown in FIG. 33 to the second position, the high pressure refrigerantthat is discharged from the compressor 4 and flowed into the highpressure space S2 by way of the outlet pipe 5 flows into the outdoorheat exchanger 9B through the pipe 8 and then, this refrigerant flowsback to the inlet of the compressor 4 by way of the throttle 10, theindoor heat exchanger 9A, the pipe 7, closed space S1 and the inlet pipe6, thereby the refrigerating cycle A is in the cooling mode.

At this time, in the slide-type four-way selector valve 43, accompanyingwith that the piston cylinder 12 and the second piston cylinder 12′ moveto the second position, the subvalve 12 ₂ closes the valve seat 3 a thathas been opened while the second subvalve 12 ₂′ opens the valve seat 2 athat has been closed, therefore by the high pressure refrigerant flowedfrom the high pressure space S2 through the through hole 12 ₁′ of thesecond piston cylinder 12′, the refrigerant pressure in the secondpressure-transducing chamber R₅ gradually increases.

Then, in the three-way selector valve 44, since the pressure of therefrigerant in the large diameter cylinder 1 h that communicates withthe second pressure-transducing chamber R₅ through the valve seat 2 aopened by the second subvalve 12 ₂′ and the channel 14G is higher thanthat in the small diameter cylinder 1 f that communicates with the inletpipe 6 through the channel 14F, due to a difference between the pressureof the refrigerant in the large diameter cylinder 1 g and that in thelarge diameter cylinder 1 h, a force stronger than the elastic force ofthe coil spring 44 j is applied to the slide shaft 44 d from the largediameter cylinder 1 h side.

Accordingly, the slide shaft 44 d moves toward the large diametercylinder 1 g side, then the coil spring 44 j is compressed and storesthe energizing force to energize the piston 44 c toward the largediameter cylinder 1 h side.

Thereafter, when the operation of the compressor 4 is halted, in thethree-way selector valve 44, due to the energizing force stored in thecoil spring 44 j, the pistons 44 b and 44 c together with the slideshaft 44 d move toward the large diameter cylinder 1 h side to besituated at the second position, while in the slide-type four-wayselector valve 43, the piston cylinder 12 and the second piston cylinder12′ are kept staying at their second position.

Then, the small diameter cylinder 1 f of the three-way selector valve 44communicating with the inlet pipe 6 through the channel 14F communicateswith the large diameter cylinder 1 h through the valve port 1 m that isopened by the piston 44 b situated at the second position. The largediameter cylinder 1 h communicates with the second pressure-transducingchamber R₅ of the slide-type four-way selector valve 43 through thevalve seat 2 a opened by the second subvalve 12 ₂′ and the channel 14G,thereby the inlet pipe 6 communicates with the secondpressure-transducing chamber R₅ through the three-way selector valve 44.

In this state, if the compressor 4 starts to operate, the high pressurerefrigerant discharged from the compressor 4 flows into the highpressure space S2 of the slide-type four-way selector valve 43 by way ofthe outlet pipe 5, then further flows into the outdoor heat exchanger 9Bthrough the pipe 8 and then, this refrigerant flows into the closedspace S1 through the throttle 10, the indoor heat exchanger 9A and thepipe 7, then flows back to the inlet of the compressor 4 by way of theinlet pipe 6, thereby the refrigerating cycle A is in the cooling mode.

At this time, since an amount of the refrigerant that can pass throughthe through hole 12 ₁′ of the second piston cylinder 12′ is small, anincrement in the pressure of the refrigerant in the secondpressure-transducing chamber R₅ of the slide-type four-way selectorvalve 43 upon starting of the operation of the compressor 4 is small,therefore a difference in the pressure between the refrigerant in thesecond pressure-transducing chamber R₅ communicating with the inlet pipe6 through the three-way selector valve 44 and the refrigerant in thehigh pressure space S2 becomes large.

Therefore, the piston cylinder 12 and the second piston cylinder 12′ ofthe slide-type four-way selector valve 43 move from the second positionto the first position shown in FIG. 33, the high pressure refrigerantthat is discharged from the compressor 4 and flowed into the highpressure space S2 by way of the outlet pipe 5 flows into the indoor heatexchanger 9A through the pipe 7 and then, this refrigerant flows back tothe inlet of the compressor 4 by way of the throttle 10, the outdoorheat exchanger 9B, the pipe 8, closed space S1 and the inlet pipe 6,thereby the refrigerating cycle A is in the heating mode.

At this time, in the slide-type four-way selector valve 43, accompanyingwith that the piston cylinder 12 and the second piston cylinder 12′ moveto the first position, the subvalve 12 ₂ opens the valve seat 3 a thathas been closed while the second subvalve 12 ₂′ closes the valve seat 2a that has been opened, therefore by the high pressure refrigerantflowed from the high pressure space S2 through the through hole 12 ₁ ofthe piston cylinder 12, the refrigerant pressure in thepressure-transducing chamber R₂ gradually increases.

Then, in the three-way selector valve 44, since the pressure of therefrigerant in the large diameter cylinder 1 g that communicates withthe pressure-transducing chamber R₂ through the valve seat 3 a opened bythe second subvalve 12 ₂ and the channel 14H is higher than that in thesmall diameter cylinder 1 f that communicates with the inlet pipe 6through the channel 14F, due to a difference between the pressure of therefrigerant in the large diameter cylinder 1 g and that in the largediameter cylinder 1 h, a force stronger than the elastic force of thecoil spring 44 k is applied to the slide shaft 44 d from the largediameter cylinder 1 g side.

Accordingly, the slide shaft 44 d moves toward the large diametercylinder 1 h side, then the coil spring 44 k is compressed and storesthe energizing force to energize the piston 44 b toward the largediameter cylinder 1 g side.

Thereafter, when the operation of the compressor 4 is halted, in thethree-way selector valve 44, due to the energizing force stored in thecoil spring 44 k, the pistons 44 b and 44 c together with the slideshaft 44 d move toward the large diameter cylinder 1 g side to besituated at the first position, while in the slide-type four-wayselector valve 43, the piston cylinder 12 and the second piston cylinder12′ are kept staying at the first position.

Thus, according to the thirteenth embodiment, the slide-type four-wayselector valve 43, which makes the piston cylinder 12 and the secondpiston cylinder 12′ select to be either the first position or the secondposition by using a difference between the pressure of the refrigerantin the high pressure space S2 and that in either thepressure-transducing chamber R₂ or the second pressure-transducingchamber R₅, performs its selector operation by using the three-wayselector valve 44, which makes the inlet pipe 6 communicate with eitherthe pressure-transducing chamber R₂ or the second pressure-transducingchamber R₅ by using the energizing force stored during the operation ofthe compressor 4.

Therefore, the heating mode, in which the refrigerant discharged fromthe outlet pipe 5 is supplied to the indoor heat exchanger 9A by way ofthe pipe 7, and the cooling mode, in which the refrigerant dischargedfrom the outlet pipe 5 is supplied to the outdoor heat exchanger 9B byway of the pipe 8, can be selected by controlling the number of times ofthe operation start of the compressor 4 and the selected state can bemaintained without using any exclusive power source such as anelectromagnetic solenoid.

Moreover, according to the thirteenth embodiment, since the selection ofcommunication for the outlet pipe 5 and the inlet pipe 6 of theslide-type four-way selector valve 43 is performed according to a startand halt of the operation of the compressor 4, neither power source foran electric drive nor control by an electric signal for selecting thechannel of the refrigerant is needed, therefore, the channel selectorvalve according to the thirteenth embodiment is advantageous.

In the thirteenth embodiment described above, the present invention isapplied to the slide-type four-way selector valve 43, in which thethrough holes 12 ₁ and 12 ₁′ are provided in the piston cylinder 12 andthe second piston cylinder 12′, respectively. Instead, the presentinvention can also be applied to a slide-type four-way selector valve,in which no through hole is provided in the piston cylinder.

In the following, such a channel selector valve mentioned right aboveaccording to a fourteenth embodiment of the present invention will beexplained with reference to FIG. 34.

FIG. 34 is a view illustrating a schematic constitution of arefrigerating cycle A employing the channel selector valve according tothe fourteenth embodiment of the present invention, in which the sameabbreviation numerals with those used for the corresponding identicalmembers or parts of the channel selector valve according to thethirteenth embodiment shown in FIG. 33 are used.

The channel selector valve according to the fourteenth embodiment, anoperational state in the cooling mode of which is shown in FIG. 34 byits sectional view, is different from the channel selector valveaccording to the thirteenth embodiment shown in FIG. 33 in points thatthe through holes 12 ₁ and 12 ₁′ in the piston cylinder 12 and thesecond piston cylinder 12′, respectively, are omitted in the slide-typefour-way selector valve 43 and that the subvalves 12 ₂ and 12 ₂′ arealso omitted in the slide-type four-way selector valve 43.

Moreover, the channel selector valve according to the fourteenthembodiment is different from the channel selector valve according to thethirteenth embodiment shown in FIG. 33 in points that a three-wayselector valve (corresponding to the pilot valve) 45, which functions asa pilot valve of the slide-type four-way selector valve 43, is providedinstead of the three-way selector valve 44.

The three-way selector valve 45 comprises a housing (corresponding tothe second housing) 45 a, to which each one end of channels 14F, 14G and14H is connected, and a piston (corresponding to the selector valveelement) 45 r, which makes the channel 14F communicate with either thechannel 14G or the channel 14H.

The housing 45 a has a cylindrical shape, in which a large diametercylinder 45 b is sandwiched by two small diameter cylinders 45 c and 45d, and a slide shaft 45 e is received in the housing 45 a so as to bemovable in a thrust direction.

In the small diameter cylinder 45 c, there is received a coil spring(corresponding to fourth storing means for storing energizing force) 45f, which energizes the slide shaft 45 e toward the small diametercylinder 45 d side, while in the small diameter cylinder 45 d, there isreceived a coil spring (corresponding to third storing means for storingenergizing force) 45 g, which energizes the slide shaft 45 e toward thesmall diameter cylinder 45 c side.

On a circumferential surface of the slide shaft 45 e, there are formedcircular grooves 45 h and 45 j leaving a space therebetween in an axialdirection, then one end surface of the slide shaft 45 e communicateswith the circular groove 45 h near said one end surface through achannel 45 k formed in the slide shaft 45 e, while an opposite endsurface of the slide shaft 45 e communicates with the circular groove 45j near said opposite end surface through a channel 45 m formed in theslide shaft 45 e.

In addition, between the circular grooves 45 h and 45 j of the slideshaft 45 e, stoppers 45 n and 45 p, such as E-rings, are put on theslide shaft 45 e leaving a space therebetween in an axial direction.

An outer diameter of the piston 45 r is formed larger than an innerdiameter of the small diameter cylinders 45 c and 45 d and smaller thanan inner diameter of the large diameter cylinder 45 b. The piston 45 ris received in the large diameter cylinder 45 b and attached to theslide shaft 45 e so that the piston 45 r can slide in an axial directionof the slide shaft 45 e between the stoppers 45 n and 45 p.

Between the piston 45 r and the slide shaft 45 e, there is provided anO-ring 45 s for sealing.

Each opposite end of the channels 14G and 14H is connected to therespective small diameter cylinders 45 c and 45 d of the housing 45 a sothat each opening of the channels 14G and 14H faces the respective endsurfaces of the slide shaft 45 e, in addition, each opposite end of thechannel 14F that is branched off into two ways is connected to therespective small diameter cylinders 45 c and 45 d of the housing 45 a sothat each opening of the branched channels faces the circumferentialsurface of the slide shaft 45 e, while an outlet pipe 5 of theslide-type four-way selector valve 43 is connected to the large diametercylinder 45 b through the channel 14J.

In the three-way selector valve 45 thus constructed, as shown in FIG.34, when a force stronger than an elastic force by a coil spring 45 g isapplied to an end surface of the slide shaft 45 e at the small diametercylinder 45 c side, the slide shaft 45 e moves toward the small diametercylinder 45 d side.

Then, the piston 45 r is pushed by the stopper 45 n to close a valveport 45 v formed by a level difference between the small diametercylinder 45 d and the large diameter cylinder 45 b and moves to thesecond position where the piston 45 r opens a valve port 45 t formed bya level difference between the small diameter cylinder 45 c and thelarge diameter cylinder 45 b, thereby the channel 14J communicates withthe channel 14H through the large diameter cylinder 45 b, the valve port45 t and the small diameter cylinder 45 c.

When the piston 45 r is at the second position, the opening of thechannel 14F connected to the small diameter cylinder 45 c is closed bythe circumferential surface of the slide shaft 45 e, thereby the channel14F connected to the small diameter cylinder 45 c is insulated from thechannel 14H, while the opening of the channel 14F connected to the smalldiameter cylinder 45 d faces the circular groove 45 j of the slide shaft45 e, thereby the channel 14F connected to the small diameter cylinder45 d communicates with the channel 14G through the circular groove 45 jand the channel 45 m.

When the piston 45 r is at the second position, the coil spring 45 g ispushed by the end surface of the slide shaft 45 e at the small diametercylinder 45 d side to be compressed and is in a state to store anenergizing force to move the slide shaft 45 e toward the small diametercylinder 45 c side.

In a state of the three-way selector valve 45 shown in FIG. 34, when theforce applied to the end surface of the slide shaft 45 e at the smalldiameter cylinder 45 c side is removed, the slide shaft 45 e is pressedby the elastic force of the coil spring 45 g and moves toward the smalldiameter cylinder 45 c side.

Then, by a sliding resistance between the O-ring 45 s and the slideshaft 45 e, the piston 45 r together with the slide shaft 45 e moves tothe first position where the piston 45 r opens the valve port 45 v andcloses the valve port 45 t, thereby the channel 14J communicates withthe channel 14G through the large diameter cylinder 45 b, the valve port45 v and the small diameter cylinder 45 d.

When the piston 45 r is at the first position, the opening of thechannel 14F connected to the small diameter cylinder 45 c faces thecircular groove 45 h of the slide shaft 45 e, thereby the channel 14Fconnected to the small diameter cylinder 45 c communicates with thechannel 14H through the circular groove 45 h and the channel 45 k, whilethe opening of the channel 14F connected to the small diameter cylinder45 d is closed by the circumferential surface of the slide shaft 45 e,thereby the channel 14F connected to the small diameter cylinder 45 d isinsulated from the channel 14G.

However, in a state that the slide shaft 45 e only has slided toward thesmall diameter cylinder 45 c side by the elastic force of the coilspring 45 g, the piston 45 r does not move relatively with respect tothe slide shaft 45 e, therefore the piston 45 r abuts on the stopper 45n to be apart from the stopper 45 p while the coil spring 45 f in thesmall diameter cylinder 45 c is extended.

Then, in this state, if a force stronger than the elastic force by thecoil spring 45 f is applied to the end surface of the slide shaft 45 eat the small diameter cylinder 45 d side, only the slide shaft 45 efurther moves toward the small diameter cylinder 45 c side until thestopper 45 p abuts on the piston 45 r, thereby the stopper 45 n is awayfrom the piston 45 r toward the small diameter cylinder 45 c side.

Then, the coil spring 45 f is pushed by the end surface of the slideshaft 45 e at the small diameter cylinder 45 c side to be compressed andis in a state to store an energizing force to move the slide shaft 45 etoward the small diameter cylinder 45 d side.

In this state, if the force that has been applied to the end surface ofthe slide shaft 45 e at the small diameter cylinder 45 d side isremoved, the slide shaft 45 e moves toward the small diameter cylinder45 d side by the elastic force of the coil spring 45 f.

Then, by a sliding resistance between the O-ring 45 s and the slideshaft 45 e, the piston 45 r together with the slide shaft 45 e moves tothe second position where the piston 45 r closes the valve port 45 v andopens the valve port 45 t, thereby the channel 14J communicates with thechannel 14H through the large diameter cylinder 45 b, the valve port 45t and the small diameter cylinder 45 c.

When the piston 45 r is at the second position, the opening of thechannel 14F connected to the small diameter cylinder 45 c is closed bythe circumferential surface of the slide shaft 45 e, thereby the channel14F connected to the small diameter cylinder 45 c is insulated from thechannel 14H, while the opening of the channel 14F connected to the smalldiameter cylinder 45 d faces the circular groove 45 j of the slide shaft45 e, thereby the channel 14F connected to the small diameter cylinder45 d communicates with the channel 14G through the circular groove 45 jand the channel 45 m.

However, in a state that the slide shaft 45 e only has slided toward thesmall diameter cylinder 45 d side by the elastic force of the coilspring 45 f, the piston 45 r does not move relatively with respect tothe slide shaft 45 e, therefore the piston 45 r abuts on the stopper 45p to be apart from the stopper 45 n while the coil spring 45 g in thesmall diameter cylinder 45 d is extended.

Then, in this state, if a force stronger than the elastic force by thecoil spring 45 g is applied to the end surface of the slide shaft 45 eat the small diameter cylinder 45 c side, only the slide shaft 45 efurther moves toward the small diameter cylinder 45 d side until thestopper 45 n abuts on the piston 45 r, thereby the stopper 45 p is awayfrom the piston 45 r toward the small diameter cylinder 45 d side.

Then, the coil spring 45 g is pushed by the end surface of the slideshaft 45 e at the small diameter cylinder 45 d side to be compressed andcomes back to the state to store an energizing force to move the slideshaft 45 e toward the small diameter cylinder 45 c side as shown in FIG.34.

In the following, an operation of the channel selector valve accordingto the fourteenth embodiment constructed as described above will beexplained.

When the operation of the compressor 4 is halted, the piston cylinder 12and the second piston cylinder 12′ of the slide-type four-way selectorvalve 43 keep their positions during an ex-operation of the compressor4, while the piston 45 r of the three-way selector valve 45 has moved tothe second position if it was at the first position during anex-operation of the compressor 4, on the other hand the piston 45 r hasmoved to the first position if it was at the second position during anex-operation of the compressor 4.

As shown in FIG. 34, in a state that the refrigerating cycle A is in theheating mode, if the operation of the compressor 4 is halted, the pistoncylinders 12 and the second piston cylinder 12′ of the slide-typefour-way selector valve 43 do not move and stays at the first positionshown in FIG. 34, while the piston 45 r of the three-way selector valve45 move from the second position shown in FIG. 34 to the first positionsince the force applied to the end surface of the slide shaft 45 e atthe small diameter cylinder 45 c side is removed.

Therefore, the small diameter cylinder 45 d of the three-way selectorvalve 45, which communicates with the second pressure-transducingchamber R₅ of the slide-type four-way selector valve 43 through thechannel 14G, communicates with the large diameter cylinder 45 b throughthe valve port 45 v that is opened by the piston 45 r situated at thefirst position, then the large diameter cylinder 45 b communicates withthe outlet pipe 5 through the channel 14J, thereby the outlet pipe 5communicates with the second pressure-transducing chamber R₅ through thethree-way selector valve 45.

Then, the small diameter cylinder 45 c of the three-way selector valve45, which communicates with the pressure-transducing chamber R₂ of theslide-type four-way selector valve 43 through the channel 14H,communicates with the inlet pipe 6 through the channel 45 k, thecircular groove 45 h and the channel 14F, thereby the inlet pipe 6communicates with the pressure-transducing chamber R₂ through thethree-way selector valve 45.

In this state, when the compressor 4 starts to operate, a high pressurerefrigerant discharged from the compressor 4 flows into the largediameter cylinder 45 b of the three-way selector valve 45 through theoutlet pipe 5 and the channel 14J, thereby a difference between thepressure of the refrigerant in the small diameter cylinder 45 c thatcommunicates with the channel 14F through the channel 45 k and thecircular groove 45 h and the pressure of high pressure refrigerant inthe large diameter cylinder 45 b becomes large.

Thereby, the coil spring 45 f is pushed by the end surface of the slideshaft 45 e at the small diameter cylinder 45 c side to be compressed,then the coil spring 45 f stores an energizing force to slide the slideshaft 45 e toward the small diameter cylinder 45 d side.

Moreover, since the outlet pipe 5 communicates with the secondpressure-transducing chamber R₅ through the three-way selector valve 45,the pressure of the refrigerant in the second pressure-transducingchamber R₅ increases so as to become equal to that in the high pressurespace S2, while, since the inlet pipe 6 communicates with thepressure-transducing chamber R₂ through the three-way selector valve 45,the pressure of the refrigerant in the pressure-transducing chamber R₂decreases to increase its difference from the pressure of therefrigerant in the high pressure space S2.

Therefore, the piston cylinder 12 and the second piston cylinder 12′ ofthe slide-type four-way selector valve 43 move from the first positionshown in FIG. 34 to the second position, then the high pressurerefrigerant, which is discharged from the compressor 4 and flowed intothe high pressure space S2 through the outlet pipe 5, flows into theoutdoor heat exchanger 9B from the pipe 8, then this refrigerant furtherflows into the closed space S1 by way of the throttle 10, the indoorheat exchanger 9A and the pipe 7 and then, comes back to the inlet ofthe compressor 4 through the inlet pipe 6, thereby the refrigeratingcycle A is in the cooling mode.

Thereafter, when the operation of the compressor 4 is halted, in thethree-way selector valve 45, by the energizing force stored in the coilspring 45 f, the piston 45 r together with the slide shaft 45 e movestoward the small diameter cylinder 45 d side to be situated at thesecond position, while in the slide-type four-way selector valve 43, thepiston cylinder 12 and the second piston cylinder 12′ are kept stayingat the second position.

Therefore, the small diameter cylinder 45 c of the three-way selectorvalve 45, which communicates with the pressure-transducing chamber R₂ ofthe slide-type four-way selector valve 43 through the channel 14H,communicates with the large diameter cylinder 45 b through the valveport 45 t that is opened by the piston 45 r situated at the secondposition, then the large diameter cylinder 45 b communicates with theoutlet pipe 5 through the channel 14J, thereby the outlet pipe 5communicates with the pressure-transducing chamber R₂ through thethree-way selector valve 45.

Then, the small diameter cylinder 45 d of the three-way selector valve45, which communicates with the second pressure-transducing chamber R₅of the slide-type four-way selector valve 43 through the channel 14G,communicates with the inlet pipe 6 through the channel 45 m, thecircular groove 45 j and the channel 14F, thereby the inlet pipe 6communicates with the second pressure-transducing chamber R₅ through thethree-way selector valve 45.

In this state, when the compressor 4 starts to operate, a high pressurerefrigerant discharged from the compressor 4 flows into the largediameter cylinder 45 b of the three-way selector valve 45 through theoutlet pipe 5 and the channel 14J, thereby a difference between thepressure of the refrigerant in the small diameter cylinder 45 d thatcommunicates with the channel 14F through the channel 45 m and thecircular groove 45 j and the pressure of high pressure refrigerant inthe large diameter cylinder 45 b becomes large.

Thereby, the coil spring 45 g is pushed by the end surface of the slideshaft 45 e at the small diameter cylinder 45 d side to be compressed,then the coil spring 45 g stores an energizing force to slide the slideshaft 45 e toward the small diameter cylinder 45 c side.

Moreover, since the outlet pipe 5 communicates with thepressure-transducing chamber R₂ through the three-way selector valve 45,the pressure of the refrigerant in the pressure-transducing chamber R₂increases so as to become equal to that in the high pressure space S2,while, since the inlet pipe 6 communicates with the secondpressure-transducing chamber R₅ through the three-way selector valve 45,the pressure of the refrigerant in the second pressure-transducingchamber R₅ decreases to increase its difference from the pressure of therefrigerant in the high pressure space S2.

Therefore, the piston cylinder 12 and the second piston cylinder 12′ ofthe slide-type four-way selector valve 43 move from the second positionto the first position shown in FIG. 34, then the high pressurerefrigerant, which is discharged from the compressor 4 and flowed intothe high pressure space S2 through the outlet pipe 5, flows into theindoor heat exchanger 9A from the pipe 7, then this refrigerant furtherflows into the closed space S1 by way of the throttle 10, the outdoorheat exchanger 9B and the pipe 8 and then, comes back to the inlet ofthe compressor 4 through the inlet pipe 6, thereby the refrigeratingcycle A is in the heating mode.

Thereafter, when the operation of the compressor 4 is halted, in thethree-way selector valve 45, by the energizing force stored in the coilspring 45 g, the piston 45 r together with the slide shaft 45 e movestoward the small diameter cylinder 45 c side to be situated at the firstposition, while in the slide-type four-way selector valve 43, the pistoncylinder 12 and the second piston cylinder 12′ are kept staying at thefirst position.

The channel selector valve according to the fourteenth embodimentconstracted as described above gives a similar effect with that of thechannel selector valve according to the thirteenth embodiment.

In the aforementioned embodiments from the first to the fourteenthembodiment, a channel selector valve constructed by employing athree-way selector valve and a slide-type four-way selector valve hasbeen explained. In the following, an embodiment, in which the presentinvention is applied to a rotary channel selector valve that performsits channel selector operation by rotation of a main valve element in avalve housing will be explained.

In the following, a schematic constitution of a refrigerating cycle Aemploying a rotary channel selector valve will be explained withreference to FIG. 35, in which the same abbreviation numerals with thoseused for the corresponding identical members or parts of the channelselector valve according to the thirteenth embodiment shown in FIG. 33are used.

In FIG. 35, a channel of the refrigerant in the cooling mode is shown bysolid lines while that in the heating mode is shown by broken lines. Inthis refrigerating cycle A, a place where the high pressure refrigerantdischarged from the compressor 4 is guided to and a place where therefrigerant to be sucked by the compressor 4 by way of an accumulator200 is guided from are mutually selected out of the indoor heatexchanger 9A and the outdoor heat exchanger 9B by a rotary four-wayselector valve 50, and an electrically-driven expansion valve 10A isprovided between the indoor heat exchanger 9A and the outdoor heatexchanger 9B. Pressure sensors Pc and Pc′ are disposed at the indoorheat exchanger 9A and the outdoor heat exchanger 9B, respectively, todetect each pressure, thereby a position of the movable member can bedetected. These pressure sensors may be disposed at a channel near therotary four-way selector valve 50.

In the following, a channel selector valve according to a fifteenthembodiment of the present invention, which can be used as the rotaryfour-way selector valve 50 shown in FIG. 35, will be explained withreference to FIGS. 36 to 45.

FIG. 36 is a sectional view of the channel selector valve 51 accordingto a fifteenth embodiment of the present invention, in which a columnarmain valve element 55 is received in a cylindrical valve housing 53rotatively and movable in a direction of a rotation axis, an open end ofthe valve housing 53 is closed by a valve seat 57, and a coil spring 59that energizes the main valve element 55 to be apart from the valve seat57 is received in the valve housing 53.

In detail, the valve housing 53 consists of an outer housing 53 a andtwo inner housings 53 b and 53 c upper and lower, out of which the outerhousing 53 a has a cylindrical shape with one end open and an oppositeend closed, the opposite end of the outer housing 53 a is connected tothe outlet pipe 5.

The inner housings 53 b and 53 c have a cyrindrical shape and an outerdiameter so as to be received inside of the outer housing 53 a. As shownin FIG. 37, at one end of the upper inner housing 53 b, a first inclinedend surface 53 d and a second inclined end surface 53 e are formed twofor each alternately in a circumferential direction of the upper innerhousing 53 b such that a peak and a valley are continued with a cycle of90°, while at one end of the second inclined end surface 53 e, whichconstitutes the valley in combination with one end of the first inclinedend surface 53 d, there is formed a groove 53 f extending in an axialdirection of the upper inner housing 53 b.

As shown in FIG. 38, the lower inner housing 53 c is constituted up anddown symmetrical with respect to the upper inner housing 53 b.

Then, as shown in FIG. 39, the upper and lower inner housings 53 b and53 c are received in the outer housing 53 a on a condition that the endsof them are faced with each other so that the peak fits with the valley.

Then, as shown in FIG. 39, a first cam groove 53 g is formed between thefirst inclined end surface 53 d of the upper inner housing 53 b and thesecond inclined end surface 53 e of the lower inner housing 53 c,likewise a second cam groove 53 h is formed between the second inclinedend surface 53 e of the upper inner housing 53 b and the first inclinedend surface 53 d of the lower inner housing 53 c.

Therefore, as shown in FIG. 36, when the upper and lower inner housings53 b and 53 c are received in the outer housing 53 a to constitute thevalve housing 53, a cam groove 53 j, consisting of the first and secondcam grooves 53 g and 53 h and the groove 53 f, is formed on an innercircumferential surface of the valve housing 53.

As shown in FIG. 40, in the valve seat 57, there are formed a firstselector port 57 a to which the pipe 7 is connected from the bottom sideand a second selector port 57 b to which the pipe 8 is connected fromthe bottom side, at positions facing with each other sandwiching acenter of the valve seat 57, in addition, two ports 57 c of the lowpressure side are formed at positions shifted by a phase of 90° in acircumferential direction of the valve seat 57 from the first and secondselector ports 57 a and 57 b, then each of two ports 57 c of the lowpressure side are connected to a respective pipe out of two pipes, whichare formed by branching the inlet pipe 6, from the bottom side of thevalve seat 57.

As shown in FIG. 40, a ring-shape groove 57 e is formed near a peripheryof the valve seat 57, into which an end of the coil spring 59 isinserted, then in this ring-shape groove 57 e, there is received athrust bearing (corresponding to slide means) 58 to prevent a pinchbetween one end of the coil spring 59 and the bottom of the ring-shapegroove 57 e from occurring and to smooth a rotation of the main valveelement 55 with respect to the valve housing 53, when an opposite end ofthe coil spring 59 adheres to the main valve element 55 and rotatestogether with the main valve element 55.

As shown in FIG. 41, the main valve element 55 is provided with alow-pressure side communication groove 55 a and a high-pressure sidecommunication channel 55 b.

The low pressure side communication groove 55 a is formed to be openedat an end surface of the main valve element 55 at the valve seat 57side, and when said end surface abuts on the valve seat 57, at a firstrotation position of the main valve element 55, the first selector port57 a and the two ports 57 c of the low pressure side communicate witheach other by the low pressure side communication groove 55 a, while ata second rotation position of the main valve element 55, the secondselector port 57 b and the two ports 57 c of the low pressure sidecommunicate with each other by the low pressure side communicationgroove 55 a.

As shown in FIG. 36, the high pressure side communication channel 55 bhas a chamber 55 d, which is opened at an opposite end to the valve seat57 side of the main valve element 55 through the valve port 55 c, and aninner channel 55 e shown in FIG. 41, then this inner channel 55 e isopened at an end surface of the main valve element 55 at the valve seat57 side keeping away from the low pressure side communication groove 55a and communicates with the chamber 55 d in the main valve element 55.

As shown in FIG. 36, a shaft 55 f is inserted into the center of themain valve element 55 to be movable in an axial direction, and when thevalve element 55 is apart from the valve seat 57, an assistant valveelement 55 g attached to an end of the shaft 55 f at the valve port 55 cside closes the valve port 55 c to make the high pressure sidecommunication channel 55 b be isolated, then an end of the shaft 55 fabuts on the valve seat 57 allowing the assistant valve element 55 g toopen the valve port 55 c when the main valve element 55 is seated on thevalve seat 57, as shown in FIGS. 42 and 43, thereby the high pressureside communication channel 55 b is in an opened state.

There are provided each guide pin (corresponding to cam follower pins)55 h at a circumferential surface position and a position shifted by aphase of 180° therefrom of the main valve element 55. As shown in FIG.36, these guide pins 55 h are inserted into the cam groove 53 j under acondition that the main valve element 55 is received in the valvehousing 53.

In the following, an operation of the channel selector valve 51according to the fifteenth embodiment constructed as described abovewill be explained.

When the operation of the compressor 4 is halted, as shown in FIG. 36,the main valve element 55 is apart from the valve seat 57 due to theenergizing force of the coil spring 59, then the assistant valve element55 g closes the valve port 55 c, while the two guide pins 55 h of themain valve element 55 are situated at the groove 53 f of the upper innerhousing 53 b, at which divisions of 90° and 270° are shown in FIG. 44,i.e. at which the cam groove 53 j of the cam housing 53 is the farthestapart from the valve seat 57.

In FIG. 44, the divisions of angle indicate a rotational position of theguide pin 55 h in the cam groove 53 j.

In the refrigerating cycle A is in the heating mode, when the operationof the compressor 4 is halted and each guide pin 55 h is situated at thegroove 53 f of the upper inner housing 53 b where the divisions of 90°or 270° are shown in FIG. 44, as shown in a figure at the right end ofFIG. 45, the low pressure side communication groove 55 a of the mainvalve element 55 faces the first and second selector ports 57 a and 57b, respectively, of the valve seat 57.

In this state, when the compressor 4 starts to operate, since theassistant valve element 55 g closes the valve port 55 c, the highpressure refrigerant flowed into the valve housing 53 from thecompressor 4 acts so as to move the main valve element 55 toward thevalve seat 57 side against the energizing force of the coil spring 59.

Then, each guide pin 55 h situated at the groove 53 f of 90° (or 270°)of the upper inner housing 53 b moves on the second cam groove 53 halong the first inclined end surface 53 d of the lower inner housing 53c, then is situated at the groove 53 f of the lower inner housing 53 c,at which the angle divisions of 180° (or 0°) is shown in FIG. 44.

Then, as each guide pin 55 h moves on the second cam groove 53 h, themain valve element 55 moves toward the valve seat 57 side with rotating,and when rotates by 90°, as shown in FIG. 42, the main valve element 55sits down on the valve seat 57 to reach the first position, thereby anend of the shaft 55 f abuts on the valve seat 57 allowing the assistantvalve element 55 g to open the valve port 55 c.

In this situation, as shown in a figure at left end of FIG. 45, the lowpressure side communication groove 55 a faces the first selector port 57a and the two low pressure side ports 57 c, while the inner channel 55 efaces the second selector port 57 b.

Therefore, as shown in FIG. 42, the outlet pipe 5 communicates with thepipe 8 through the high pressure side communication channel 55 b and thesecond selector port 57 b, while the inlet pipe 6 communicates with thepipe 7 through the low pressure side communication groove 55 a and thetwo low pressure side ports 57 c.

Consequently, the high pressure refrigerant from the compressor 4 flowsinto the outdoor heat exchanger 9B from the pipe 8 by way of the outletpipe 5, high pressure side communication channel 55 b and the secondselector port 57 b, then passes through the throttle 10, the indoor heatexchanger 9A, pipe 7, the first selector port 57 a, the low pressureside communication groove 55 a, the two low pressure side ports 57 c andthe inlet pipe 6, and finally comes back to the inlet of the compressor4, thereby the refrigerating cycle A is in the cooling mode.

Thereafter, when the operation of the compressor 4 is halted, thepressure of the refrigerant flowed into the valve housing 53 decreases,thereby the energizing force of the coil spring 59 acts to move the mainvalve element 55 being away from the valve seat 57.

Then, each guide pin 55 h situated at the groove 53 f of 180° (or 0°) ofthe lower inner housing 53 moves on the first cam groove 53 g along thefirst inclined end surface 53 d of the upper inner housing 53 b, then issituated at the groove 53 f of 270° (or 90°) of the upper inner housing53 b.

Then, as each guide pin 55 h moves on the first cam groove 53 g, themain valve element 55 moves toward the outlet pipe 5 side with rotatingin the valve housing 53, and when rotates by 90°, the main valve element55 reaches a first intermediate position where the main valve element isthe farthest away from the valve seat 57, thereby the assistant valveelement 55 g of the shaft 55 f, an end of which is apart from the valveseat 57, closes the valve port 55 c.

In this situation, as shown in the second figure from the left of FIG.45, the low-pressure side communication groove 55 a faces the first andsecond selector ports 57 a and 57 b, respectively.

In this state, when the compressor 4 starts to operate, each guide pin55 h situated at the groove 53 f of 270° (or 90°) of the upper innerhousing 53 b moves on the second cam groove 53 h, then is situated atthe groove 53 f of 0° (or 180°) of the lower inner housing 53 c.

Then, as each guide pin 55 h moves on the second cam groove 53 h, themain valve element 55 moves toward the valve seat 57 side with rotatingin the valve housing 53, and when rotates by 90°, as shown in FIG. 43,the main valve element 55 sits down on the valve seat 57 to reach thesecond position, thereby an end of the shaft 55 f abuts on the valveseat 57 allowing the assistant valve element 55 g to open the valve port55 c.

In this situation, as shown in a second figure from the right end ofFIG. 45, the low pressure side communication groove 55 a faces thesecond selector port 57 b and the two low pressure side ports 57 c,while the inner channel 55 e faces the first selector port 57 a.

Therefore, as shown in FIG. 43, the outlet pipe 5 communicates with thepipe 7 through the high pressure side communication channel 55 b and thefirst selector port 57 a, while the inlet pipe 6 communicates with thepipe 8 through the second selector port 57 b, the low pressure sidecommunication groove 55 a and the two low pressure side ports 57 c.

Consequently, the high pressure refrigerant from the compressor 4 flowsinto the indoor heat exchanger 9A from the pipe 7 by way of the outletpipe 5, high pressure side communication channel 55 b and the firstselector port 57 a, then passes through the throttle 10, the outdoorheat exchanger 9B, pipe 8, the second selector port 57 b, the lowpressure side communication groove 55 a, the two low pressure side ports57 c and the inlet pipe 6, and finally comes back to the inlet of thecompressor 4, thereby the refrigerating cycle A is in the heating mode.

Thereafter, when the operation of the compressor 4 is halted, thepressure of the refrigerant flowed into the valve housing 53 decreases,thereby the energizing force of the coil spring 59 acts to move eachguide pin 55 h, situated at the groove 53 f of 0° (or 180°) of the lowerinner housing 53 c, on the first cam groove 53 g so as to be situated atthe groove 53 f of 90° (or 270°) of the upper inner housing 53 b.

Then, as each guide pin 55 h moves on the first cam groove 53 g, themain valve element 55 moves toward the outlet pipe 5 side with rotatingin the valve housing 53, and when rotates by 90°, as shown in FIG. 36,the main valve element 55 reaches a second intermediate position wherethe main valve element 55 is the farthest away from the valve seat 57,thereby the assistant valve element 55 g of the shaft 55 f, an end ofwhich is apart from the valve seat 57, closes the valve port 55 c.

Thereby, as shown in a figure at the right end of FIG. 45, the systemcomes back to an initial state, in which the low pressure communicationgroove 55 a faces the first and second valve ports 57 a and 57 b,respectively.

Thus according to the channel selector valve 51 of the fifteenthembodiment, by using a differential pressure generated due to therefrigerant flow discharged from the compressor 4 and the energizingforce due to the coil spring 59 disposed between the main valve element55 and the valve seat 57, the main valve element 55 is moved in thedirection nearer to or away from the valve seat 57, while each guide pin55 h is moved along the cam groove 53 j and the main valve element 55 isallowed to rotate with respect to the valve housing 53, thereby the mainvalve element 55 is moved between the first and second positions.

Therefore, a place, with which the outlet pipe 5 or the inlet pipe 6communicates is selected through the low pressure side communicationgroove 55 a and the high pressure side communication channel 55 b, isselected between either the first selector port 57 a or the secondselector port 57 b of the valve seat 57, thereby the heating mode, inwhich the refrigerant discharged from the outlet pipe 5 is supplied tothe indoor heat exchanger 9A by way of the pipe 7, and the cooling mode,in which the refrigerant discharged from the outlet pipe 5 is suppliedto the outdoor heat exchanger 9B by way of the pipe 8, can be selectedby starting and halting the operation of the compressor 4, and theselected state can be maintained without using any exclusive powersource such as an electromagnetic solenoid.

Moreover, according to the fifteenth embodiment, since the selection ofcommunication for the outlet pipe 5 and the inlet pipe 6 in the channelselector valve 51 is performed according to a start and halt of theoperation of the compressor 4, neither power source for an electricdrive nor control by an electric signal for selecting the channel of therefrigerant is needed, therefore, the channel selector valve 51according to the fifteenth embodiment is advantageous.

In addition, in the channel selector valve 51 according to the fifteenthembodiment, the groove 53 f of the cam groove 53 j formed in the valvehousing 53 is provided not at a junction between an end of the firstinclined end surface 53 d and an end of the second inclined end surface53 e but at the end of the second inclined end surface 53 e, thereby thechannel selector valve 51 has an advantage as follows.

That is, when the main valve element 55 moves in the direction nearer toor away from the valve seat 57, each guide pin 55 h, which has movedfrom the first inclined end surface 53 d to the groove 53 f, isprevented from coming back to the first inclined end surface 53 d and issecurely moved to the second inclined end surface 53 e, then therotational direction of the main valve element 55 is limited to onedirection, thereby the selection of the modes of the refrigerating cycleA can be securely performed by controlling the number of start and haltof the operation of the compressor 4.

In the channel selector valve 51 according to the fifteenth embodimentdescribed above, the movement of the main valve element 55 in thedirection away from the valve seat 57 is performed by the energizingforce of the coil spring 59 disposed between the main valve element 55and the valve seat 57. Instead, like a channel selector valve 61according to a sixteenth embodiment of the present invention shown inFIG. 46, a position of the valve housing 53 may be set upside down suchthat the outlet pipe 5 is situated below in a vertical direction, thenthe movement of the main valve element 55 in the direction away from thevalve seat 57 may be performed by an own weight of the main valveelement 55.

If the channel selector valve 61 is constructed as described above, theassistant valve element 55 g opens the valve port 55 c by an own weightof the shaft 55 f even if the main valve element 57 does not sit down onthe valve seat 57, after the high pressure refrigerant discharged fromthe compressor 4 flows into the valve housing 53 through the outlet pipe5 upon the start of the operation of the compressor 4, the assistantvalve element 55 g opens the valve port 55 c against the own weight ofthe shaft 55 f, by the pressure of the high pressure refrigerant flowedinto the valve housing 53, until the main valve element 55 sits down onthe valve seat 57.

The channel selector valve 61 according to the sixteenth embodimentconstracted as described above gives a similar effect with that of thechannel selector valve 51 according to the fifteenth embodiment.Moreover, in the channel selector valve 61 according to the sixteenthembodiment, since the movement of the main valve element 55 in thedirection away from the valve seat 57 is performed by an own weight ofthe main valve element 55, the coil spring 59 can be omitted, resultingin a reduction of the cost of the channel selector valve.

As shown in FIG. 47, in a channel selector valve 71 according to theseventeenth embodiment of the present invention, the coil spring 59provided between the main valve element 55 and the valve seat 57, whichis employed in the channel selector valve 51 according to the fifteenthembodiment shown in FIG. 36, is replaced by a second coil spring 73provided between the main valve element 55 and an closed end of theouter housing 53 a, to which the outlet pipe 5 is connected, thereby themain valve element 55 is energized toward the valve seat 57 side by anenergizing force due to the second coil spring 73.

When the channel selector valve 71 is constructed as described above,the movement of the main valve element 55 between the first and thesecond positions is performed in such a manner that the compressor 4,the outlet of which is connected to the outlet pipe 5, is operated in adirection of inverse rotation so as to decrease the pressure of therefrigerant existed in a space between the closed end of the outerhousing 53 a and the main valve element 55, thereby the main valveelement 55 is moved in the direction away from the valve seat 57 againstthe energizing force of the second coil spring 73.

The channel selector valve 71 according to the seventeenth embodimentconstracted as described above gives a similar effect with that of thechannel selector valve 51 according to the fifteenth embodiment.Moreover, in the channel selector valve 71 according to the seventeenthembodiment, since the main valve element 55 moves between the first andthe second positions even if the compressor 4 is not rotated in a normaldirection, when the refrigerating cycle A is operated again in the sameoperational mode with the former mode, no pre-operation of thecompressor 4 with the rotation in a normal direction is needed for achannel selection, i.e. the so-called dummy operation of the compressor4 can be omitted, therefore the channel selector valve 71 isadvantageous in this respect.

In the following, a channel selector valve according to a eighteenthembodiment of the present invention, which can be employed as the rotaryfour-way selector valve 50 shown in FIG. 35, will be explained withreference to FIGS. 48 to 53.

FIG. 48 is a sectional view of a channel selector valve according to theeighteenth embodiment of the present invention, in which the sameabbreviation numerals with those used for the corresponding identicalmembers or parts of the channel selector valve 51 according to thefifteenth embodiment shown in FIG. 36 are used.

The channel selector valve 81 according to the eighteenth embodimentshown in FIG. 48 is different from the channel selector valve 51according to the fifteenth embodiment shown in FIG. 36 in a point that asecond coil spring 73 is provided between the main valve element 55 andan closed end of the outer housing 53 a, to which the outlet pipe 5 isconnected, so as to energize the main valve element 55 to move in thedirection nearer to the valve seat 57, and except this point the channelselector valve 81 is constructed similarly to the channel selector valve51.

In the channel selector valve 81 according to the eighteenth embodimentconstructed as described above, when the operation of the compressor 4is halted, the main valve element 55 is situated at an intermediateposition in a region of its movement in the direction nearer to or awayfrom the valve seat 57, by a balance between an energizing force due tothe coil spring 59 and that due to the second coil spring 73, while eachguide pin 55 h is situated at an intermediate position between the firstcam groove 53 g and the second cam groove 53 h of the cam groove 53 j asshown in FIGS. 49 and 51.

Divisions of angle of FIG. 44 indicate a rotational position of theguide pin 55 h of the main valve element 55 in the cam groove 53 j.

When the operation of the compressor 4 is halted after the refrigeratingcycle A has been in the cooling mode, and assuming that each guide pinis situated at an intermediate position of the first cam groove 53 gwhere is forward by 30° from the groove 53 f of the upper inner housing53 b at which a division 90° (or 270°) is shown in FIG. 49, when thecompressor 4 starts to operate, the following steps will take place.

That is, since the assistant valve element 55 g closes the valve port 55c, the high pressure refrigerant flowed into the valve housing 53 fromthe compressor 4 acts to move the main valve element 55 toward the valveseat 57 side against the energizing force of the coil spring 59.

Then, each guide pin 55 h situated at an intermediate position of thefirst cam groove 53 g moves on the first cam groove 53 g along thesecond inclined end surface 53 e of the lower inner housing 53 c, thenis situated at the groove 53 f of 0° (or 180°) of the lower innerhousing 53 c, while the main valve element 55 sits down on the valveseat 57 to reach the first position as shown in FIG. 50, thereby therefrigerating cycle A is in the cooling mode.

Thereafter, when the operation of the compressor 4 is halted, since thepressure of the refrigerant flowed into the valve housing 53 decreases,the energizing force of the coil spring 59 acts to part the main valveelement 55 from the valve seat 57.

Then, each guide pin 55 h, situated at the groove 53 f of 0° (180°) ofthe lower inner housing 53 c, moves on the first cam groove 53 g alongthe first inclined end surface 53 d of the upper inner housing 53 b andcomes back to an intermediate position of the first cam groove 53 gshown in FIG. 49, thereby the main valve element 55 comes back to theintermediate position where the energizing force of the coil spring 59balances with that of the second coil spring 73.

Thereafter, when the compressor 4 starts to operate again, the mainvalve element 55 comes back to the first position similarly to theoperation described above, thereby the refrigerating cycle A is in thecooling mode.

To the contrary, when the compressor 4 is operated in a direction ofinverse rotation, the pressure of the refrigerant existed in a spacebetween the closed end of the outer housing 53 a and the main valveelement 55 is decreased, thereby the main valve element 55 is moved inthe direction away from the valve seat 57 against the energizing forceof the second coil spring 73.

Then, each guide pin 55 h situated at an intermediate position of thefirst cam groove 53 g moves on the first cam groove 53 g along the firstinclined end surface 53 d of the upper inner housing 53 b, then issituated at the groove 53 f of the upper inner housing 53 b where adivision of 90° (or 270°) is shown in FIG. 51.

While the main valve element 55 reaches a point where is the farthestaway from the valve seat 57 as shown in FIG. 52.

Thereafter, when the operation of the compressor 4 is halted, since thedecrease in the pressure of the refrigerant in the space between theclosed end of the outer housing 53 a and the main valve element 55becomes zero, the main valve element 55 moves in the direction nearer tothe valve seat 57 by the energizing force of the second coil spring 73.

Then, each guide pin 55 h situated at the groove 53 f of 90° (or 270°)of the upper inner housing 53 b moves on the second cam groove 53 h,then is situated at an intermediate position of the second cam groove 53h, at which each guide pin 55 h proceeds by 30° toward the groove 53 fof 180° (or 0°) of the lower inner housing 53 c side as shown in FIG.51, thereby the main valve element 55 further rotates by 60° from thestate shown in FIG. 48 so as to reach said intermediate position.

Thereafter, when the compressor 4 starts to operate again, since theassistant valve element 55 g closes the valve port 55 c, the highpressure refrigerant flowed into the valve housing 53 from thecompressor 4 acts to move the main valve element 55 toward the valveseat 57 side against the energizing force of the coil spring 59.

Then, each guide pin 55 h situated at an intermediate position of thesecond cam groove 53 h moves on the second cam groove 53 h along thefirst inclined end surface 53 d of the lower inner housing 53 c, then issituated at the groove 53 f of 180° (or 0°) of the lower inner housing53 c, while the main valve element 55 sits down on the valve seat 57 toreach the second position as shown in FIG. 53, thereby the refrigeratingcycle A is in the heating mode.

Thereafter, when the operation of the compressor 4 is halted, since thepressure of the refrigerant flowed into the valve housing 53 decreases,the energizing force of the coil spring 59 acts to part the main valveelement 55 from the valve seat 57.

Then, each guide pin 55 h, situated at the groove 53 f of 180° (0°) ofthe lower inner housing 53 c, moves on the first cam groove 53 g andreaches to an intermediate position of the first cam groove 53 g, atwhich each guide pin 55 h proceeds by 60° toward the groove 53 f of 270°(or 90°) of the upper inner housing 53 b side as shown in FIG. 51,thereby the main valve element 55 further rotates by 180° from the stateshown in FIG. 48 so as to reach said intermediate position.

Thereafter, the compressor 4 starts to operate again, by the highpressure refrigerant flowed into the valve housing 53, the main valveelement 55 moves in the direction nearer to the valve seat 57 againstthe energizing force of the coil spring 59.

Then, each guide pin 55 h situated at an intermediate position of thefirst cam groove 53 g shown in FIG. 51 moves on the first cam groove 53g along the second inclined end surface 53 e of the lower inner housing53 c and comes back to the groove 53 f of 180° (or 0°) of the lowerinner housing 53 c, while the main valve element 55 comes back to thesecond position shown in FIG. 53, thereby the refrigerating cycle A isin the heating mode.

To the contrary, when the compressor 4 is operated in a direction ofinverse rotation, the pressure of the refrigerant existed in a spacebetween the closed end of the outer housing 53 a and the main valveelement 55 is decreased, and the main valve element 55 moves in thedirection away from the valve seat 57 against the energizing force ofthe second coil spring 73, then each guide pin 55 h, which has beensituated at an intermediate position of the first cam groove 53 g shownin FIG. 51, is situated at the groove 53 f of 270° (or 90°) of the upperinner housing 53 b.

Then, the main valve 55 further rotates by 180° from the state shown inFIG. 52 and reaches the farthest position from the valve seat 57.

Thereafter, when the operation of the compressor 4 is halted, each guidepin 55 h moves on the second cam groove 53 h from the groove 53 f of270° (or 90°) of the upper inner housing 53 b and is situated at anintermediate position of the second cam groove 53 h, at which each guidepin 55 h proceeds by 30° toward the groove 53 f of 0° (or 180°) of thelower inner housing 53 c side, thereby the main valve element 55 furtherrotates by 240° from the state shown in FIG. 48 and reaches saidintermediate position.

Then, when the compressor 4 starts to operate again, by the highpressure refrigerant flowed into the valve housing 53, the main valveelement 55 moves in the direction nearer to the valve seat 57 againstthe energizing force of the coil spring 59.

Then, each guide pin 55 h situated at an intermediate position of thesecond cam groove 53 h moves on the second cam groove 53 h along thefirst inclined end surface 53 d of the lower inner housing 53 c and issituated at the groove 53 f of 0° (or 180°) of the lower inner housing53 c, while the main valve element 55 sits down on the valve seat 57 andreaches the first position as shown in FIG. 50, thereby therefrigerating cycle A is in the cooling mode.

Thereafter, when the operation of the compressor 4 is halted, since thepressure of the refrigerant flowed into the valve housing 53 decreases,the energizing force of the coil spring 59 acts to part the main valveelement 55 from the valve seat 57, while each guide pin 55 h, which hasbeen situated at the groove 53 f of 0° (or 180°) of the lower innerhousing 53 c, moves on the first cam groove 53 g and comes back to theintermediated position of the first cam groove 53 g shown in FIG. 49,thereby the main valve element 55 comes back to said intermediateposition shown in FIG. 48.

The channel selector valve 81 according to the eighteenth embodimentconstracted as described above gives a similar effect with that of thechannel selector valve 51 according to the fifteenth embodiment.Moreover, in the channel selector valve 81 according to the eighteenthembodiment, since by using a balance between the energizing forces ofthe coil spring 59 and the second coil spring 73, the main valve element55 is situated at the intermediate position in a range of the movementin the direction nearer to or away from the valve seat 57, thereby nopre-operation of the compressor 4 with the rotation in a normaldirection is needed for a channel selection, i.e. the so-called dummyoperation of the refrigerating cycle A can be omitted similarly to thechannel selector valve 71 according to the seventeenth embodiment,therefore the channel selector valve 81 is advantageous in this respect.

In the aforementioned channel selector valves 51, 61, 71 and 81, eachguide pin 55 h of the main valve element 55 is moved along the camgroove 53 j of the housing 53 so that the movement of the main valveelement 55 in the direction nearer to or away from the valve seat 57 istransformed to the rotation of the main valve element 55 in acircumferential direction, instead the arrangement of the guide pin andthe cum groove may be set inversely between the main valve element 55and the valve housing 53.

A channel selector valve according to a nineteenth embodiment shown inFIG. 54 has such a construction mentioned just above, and in the channelselector valve 91 according to the nineteenth embodiment, a rotatingshaft 93 of a main valve element 55 is provided at the center of a valveseat 57, a cam groove 53 j is formed on the circumferential surface ofthe rotating shaft 93 as shown in FIGS. 55 and 56, then a hollow 55 k(shown in FIG. 57) into which one half of a guide ball 95 is inserted,another half of the guide ball 95 being inserted into the cam groove 53j, is formed in a shaft hole 55 j of the main valve element 55 shown inFIG. 54, into which the rotating shaft 93 is inserted.

In the channel selector valve 91 according to the nineteenth embodiment,constitutions of a low pressure side communication groove and a highpressure side communication channel of the main valve element 55 aredifferent from those of the channel selector valves 51, 61, 71 and 81according to the fifteenth to eighteenth embodiments, respectively,however the primary part of the channel selector valve 91 is theconstitution for transforming the movement of the main valve element 55in the direction nearer to or away from the valve seat 57 to therotation of the main valve element 55 in a circumferential direction andis not a structure of the main valve element 55 for channel selection,therefore an explanation of the structure of the main valve element 55will be omitted.

The channel selector valve 91 according to the nineteenth embodimentconstracted as described above gives a similar effect with that of thechannel selector valve 51 according to the fifteenth embodiment.

In the aforementioned channel selector valves 51, 61, 71, 81 and 91according to the fifteenth to nineteenth embodiments, respectively, thecam groove 53 j is formed over whole circumference of the valve housing53 and the rotating shaft 53, instead the cam groove 53 j may be formedon a partial circumference thereof.

A channel selector valve according to a twentieth embodiment shown inFIG. 58 has such a construction mentioned just above, and the channelselector valve 101 according to the twentieth embodiment is differentfrom the channel selector valve 51 according to the sixteenth embodimentshown in FIG. 36 in points that each guide pin has a rectangular shapein its top view and is attached to the main valve element 55 to moverotatively and that the cam groove 53 k on the inner circumferentialsurface of the valve housing 53 is not formed over the wholecircumference of the valve housing 53 but formed divided in twoindependently with each other.

In the channel selector valve 101 according to the twentieth embodiment,when the main valve element 55 moves in the direction nearer to or awayfrom the valve seat 57, as shown in FIG. 59, each guide pin 55 h movesback and forth in a X-shape channel along the cam groove 53 k withchanging its direction properly, thereby the main valve element 55rotatively moves back and forth within the predetermined angles withrespect to the valve housing 53.

In the channel selector valve 101 according to the twentieth embodiment,constitutions of a low pressure side communication groove and a highpressure side communication channel of the main valve element 55 andconstitutions of a port of a valve seat 57 and so on are different fromthose of the channel selector valves 51, 61, 71, 81 and 91 according tothe fifteenth to nineteenth embodiments, respectively.

However the primary part of the channel selector valve 101 is theconstitution for transforming the movement of the main valve element 55in the direction nearer to or away from the valve seat 57 to therotation of the main valve element 55 in a circumferential direction andis not a structure of the main valve element 55 or the valve seat 57 forchannel selection, therefore an explanation of the structure of the mainvalve element 55 and the valve seat 57 will be omitted.

The channel selector valve 101 according to the twentieth embodimentconstructed as described above gives a similar effect with that of thechannel selector valve 51 according to the fifteenth embodiment.

In the above, preferred embodiments of the channel selector valveaccording to the present invention are explained, then in the following,a preferred embodiment of a compressor with a channel selector valveaccording to the present invention will be explained.

FIG. 60 is a view illustrating a schematic constitution of arefrigerating cycle employing a compressor with a channel selector valveaccording to a twenty first embodiment of the present invention, inwhich the same abbreviation numerals with those used for thecorresponding identical members or parts of the refrigerating cycleaccording to the fifth embodiment shown in FIG. 9 are used.

The compressor with a channel selector valve according to a twenty firstembodiment, an operation state of which in the heating mode is shown byits sectional view in FIG. 60, is constructed by integrating the channelselector valve according to the fifth embodiment of the presentinvention shown in FIG. 9 with a compressor body 4A shown in FIG. 60.

The compressor body 4A comprises: a compressor housing 4 a; a lowpressure chamber 4 b provided in the compressor housing 4 acommunicating with the inlet pipe 6; a high pressure chamber 4 cprovided in the compressor housing 4 a and partitioned from the lowpressure chamber 4 b; and a compressing section 4 d provided in thecompressor housing 4 a, which compresses a refrigerant introduced fromthe inlet pipe 6 into the low pressure chamber 4 b and guides therefrigerant to the high pressure chamber 4 c.

The compressor body 4A constructed as described above integrates thecompressor housing 4 a part, which partitions the high pressure chamber4 c of the compressor housing 4 a in the interior thereof, with thereversing valve housing 1 in the channel selector valve according to thefifth embodiment and communicates the high pressure chamber 4 c to thehigh pressure chamber R₁ of the reversing valve housing 1.

Consequently, in the compressor body 4A, the part that partitions thehigh pressure chamber 4 c of the compressor housing 4 a in the interiorthereof functions as the outlet pipe 5 that guides a high pressurerefrigerant compressed in the compressing section 4 d to the highpressure chamber R₁ of the reversing valve housing 1.

As to the compressor with a channel selector valve according to a twentyfirst embodiment constructed as described above, the compressor body 4Ais operated similarly to the operation of the compressor 4 in therefrigerating cycle according to the fifth embodiment, thereby thepiston cylinder 12 of the reversing valve housing 1 can be selectedbetween the first and second positions.

According to the compressor with a channel selector valve of the twentyfirst embodiment thus constructed, the same effect with that of thechannel selector valve according to the fifth embodiment can beobtained, moreover, since the channel selector valve is integrated withthe compressor, a laying pipes for connection can be omitted, therebythe construction can be simplified.

The above construction prevents a leak of the refrigerant from occurringat a connection point of a pipe laying between the high pressurechambers 4 c and R₁, thereby contributing to prevention of atmosphericpollution, and since there is no current conducting part for anelectromagnetic solenoid and the like around the compressor thatgenerates oscillation, the above construction also prevents anoccurrence of an electrical fault due to failure in current conductionat an electric contact and a breaking of electric wire and the like,thereby reliance of the operation can be improved.

A channel selector valve, which is integrated with the compressor body4A to construct the compressor with a channel selector valve, is notlimited to the channel selector valve according to the fifth embodimentshown in FIG. 9, which is employed in the compressor with a channelselector valve of the twenty first embodiment, instead, may be thechannel selector valve according to the seventh embodiment of thepresent invention shown in FIG. 18, as shown in FIG. 61, i.e. a viewillustrating a schematic constitution of a refrigerating cycle employinga compressor with a channel selector valve according to a twenty secondembodiment of the present invention.

Moreover, although figures are omitted here, the channel selector valveaccording to sixth or eighth embodiment shown in FIG. 15 or 23,respectively, may be integrated with the compressor body 4A to constructthe compressor with a channel selector valve. Furthermore, each channelselector valve explained in the respective embodiment up to thetwentieth embodiment may be integrated with the compressor body 4A toconstruct the compressor with a channel selector valve.

When a channel selector valve except the channel selector valveaccording to the fifth embodiment is integrated with the compressor body4A to construct the compressor with a channel selector valve, pipes andchannels directly or indirectly connected to the pressure-transducingchamber R₂ and the second pressure-transducing chamber R₅ in eachchannel selector valve according to the respective embodiment isconnected likewise in the compressor with a channel selector valveintegrally constructed with the compressor body.

As to the compressor with the channel selector valve according to theembodiment, except the channel selector valve according to the fifthembodiment, integrally constructed with the compressor body 4A includingthe compressor with the channel selector valve according to the twentyfirst or twenty second embodiment, the channel selector valve integratedwith the compressor body 4A to construct the compressor with the channelselector valve is separately constituted from the compressor 4, then thesimilar operation with that performed with respect to the refrigeratingcycle A is performed, thereby an operation of the channel selector valvecan be carried out.

By the compressor with the channel selector valve according to theembodiment, except the channel selector valve according to the fifthembodiment, integrally constructed with the compressor body 4A includingthe compressor with the channel selector valve according to the twentyfirst or twenty second embodiment, a similar effect with that of thecompressor with the channel selector valve according to the twenty firstembodiment can be obtained.

In each embodiment mentioned above, a channel selector valve for use toreverse a channel of the refrigerant in the refrigerating cycle and acompressor with a channel selector valve in which the channel selectorvalve is integrated are explained. However, the present invention can bewidely applied to a channel selector valve for use to select a channelof various fluid, for example, liquid such as pressure oil and water orgas except refrigerant, a different type of channel selector valve or acompressor with a channel selector valve in which such a channelselector valve is integrated.

In the following, preferred embodiments of a device for controlling arefrigerating cycle according to the present invention will be explainedwith reference to the drawings.

FIG. 63 is a block diagram illustrating an example of a refrigeratingcycle according to an embodiment of the present invention, whichcomprises a heat pump-type air conditioner consisting of an indoor unit(inside of alternate long and short dash line in the figure) and anoutdoor unit (outside of alternate long and short dash line in thefigure). In FIG. 63, an abbreviation numeral 4 denotes a compressor, 9Aan indoor heat exchanger loaded in the indoor unit, 9B an outdoor heatexchanger loaded in the outdoor unit, 10A an electrically-drivenexpansion valve as a throttle device, 200 an accumulator, and 100 achannel selector valve. In the following embodiments, a word anelectrically-driven expansion valve will be used for an explanation onthe structure and a word throttle device will be used for an explanationon the function. Here, the throttle device is not limited to anelectrically-driven expansion valve and may be other constitution.

An outlet of the compressor 4 is connected to the channel selector valve100 while an inlet of the compressor 4 is connected to the channelselector valve 100 by way of the accumulator 200. The channel selectorvalve 100 is connected to the indoor heat exchanger 9A and the outdoorheat exchanger 9B through a pipe for heat exchanger while theelectrically-driven expansion valve 10A is provided between the indoorheat exchanger 9A and the outdoor heat exchanger 9B. Thereby, thecompressor 4, the channel selector valve 100, accumulator 200, theindoor heat exchanger 9A, the outdoor heat exchanger 9B and theelectrically-driven expansion valve 10A constitute the refrigeratingcycle A. In the refrigerating cycle A according to this embodiment, thechannel selector valve 100 is any one of the various types of channelselector valve according to the following embodiments.

The compressor 4 compresses the refrigerant and the compressedrefrigerant is guided into the channel selector valve 100. As will beexplained later, the channel selector valve selects a channel inresponse to an operation mode, and the refrigerant discharged from thecompressor 4 is guided into either the indoor heat exchanger 9A or theoutdoor heat exchanger 9B in response to a channel selected. That is, inthe heating mode, as shown in FIG. 63 by arrows, the compressedrefrigerant is guided from the channel selector valve 100 into theindoor heat exchanger 9A, which functions as a condenser, therefrigerant guided from the indoor heat exchanger 9A is guided into theoutdoor heat exchanger 9B, which functions as an evaporator through theelectrically-driven expansion valve 10A. Then, the refrigerantevaporated in the outdoor heat exchanger 9B is guided into thecompressor 4 by way of the channel selector valve 100 and theaccumulator 200. On the other hand, in the cooling mode, as shown bybroken lines in FIG. 63, the refrigerant compressed in the compressor 4is circulated in order of the channel selector valve 100, the outdoorheat exchanger 9B, the electrically-driven expansion valve 10A, theindoor heat exchanger 9A, the channel selector valve 100, theaccumulator 200, and the compressor 4, wherein the outdoor heatexchanger 9B functions as a condenser while the indoor heat exchanger 9Afunctions as a evaporator.

The indoor unit is provided with a cross flow fan 91A for sending airpassing through the indoor heat exchanger 9A, and a heat exchanger motor92A for rotating the cross flow fan 91A is controlled its rotation by anindoor control section 300 constituted with a microcomputer and the likethrough a driver 301, thereby a heat exchange capacity of the indoorheat exchanger 9A is controlled. An indoor temperature Ta is detected bya temperature sensor 302 while a temperature Tc of the indoor heatexchanger 9A is detected by a temperature sensor 303. A receiver section304 receives signals of a remote control 500 such as an infrared-type,thereby the selection and setting of an operation in the indoor controlsection 300 can be carried out by a remote control.

The outdoor unit is provided with a fan 91B for sending air passingthrough the outdoor heat exchanger 9B, and a heat exchanger motor 92Bfor rotating the fan 91B is controlled its rotation by an outdoorcontrol section 400 constituted with a microcomputer and the likethrough a driver 401, thereby a heat exchange capacity of the outdoorheat exchanger 9B is controlled. An outdoor temperature Ta is detectedby a temperature sensor 402 while a temperature Tc of the outdoor heatexchanger 9B is detected by a temperature sensor 403. An outdoor controlsection 400 controls an opening ratio of the electrically-drivenexpansion valve 10A through a driver 404. Further, the outdoor controlsection 400 detects a temperature Td at the outlet of the compressor 4by a temperature sensor 405 and controls the compressor 4 by athree-phase electrical power supplied from an inverter module explainedlater.

FIG. 64 is a block diagram principally illustrating an electric systemof an indoor control section 300 and outdoor control section 400. Theindoor control section 300 has a power relay 310 for performing anon-off action of a main power source. A single-phase alternating currentof 100 V is supplied to an AC/DC converter 320 through the power relay310, transformed into various predetermined direct current voltages bythe AC/DC converter 320 and supplied to a microcomputer 330 and so on.The single-phase alternating current of 100 V supplied through the powerrelay 310 is also supplied to the outdoor control section 400 through alead 21 for supplying power.

In the outdoor control section 400, an alternating current supplied ispassed through a noise filter 410, rectified in a voltage doublerrectifier circuit 420 and smoothed by a smoothing capacitor 430, therebya predetermined direct current voltage is generated. A current by thedirect current thus generated is supplied to an inverter module 450through a shunt resistor 440. A three-phase power is generated by theinverter module 450 and supplied to the compressor 4. On the other hand,an output from the smoothing capacitor 430 is transformed into apredetermined internal direct current voltage by a DC/DC converter 460and supplied to a microcomputer 470 and so on. The microcomputer 470outputs drive signals to the inverter module 450 so as to control anoperation of the compressor 4. A capacity of the compressor 4 tocompress the refrigerant is controlled by a frequency (Hz) of the drivesignal, that is, the higher the frequency (Hz), the higher the capacityof compression. For example, if set 30 Hz as a first predeterminedcapacity and 10 Hz as a second predetermined capacity, the pressure ofthe refrigerant at the first predetermined capacity is higher than thatat the second predetermined capacity. The microcomputer 470 performs aserial communication with the microcomputer 330 through a communicationlead 22 so as to carry out a transfer of data.

FIG. 62 is a block diagram according to an embodiment of a device forcontrolling a refrigerating cycle of the present invention, in whicheach element of the block diagram corresponds to the respective elementor a combination of each element in FIGS. 63 and 64. In therefrigerating cycle A, the identical element with that of FIG. 63 hasthe same abbreviation numeral with that of FIG. 63. A control device Cshown by an alternate long and short dash line in FIG. 62 corresponds tothe indoor control section 300 and the outdoor control section 400, inwhich a processing section C1 of the control device C corresponds to themicrocomputer 330 of the indoor control section 300 and themicrocomputer 470 of the outdoor control section 400. An input sectionC2 corresponds to the receiver section 304 of the indoor unit or amanual switch that is not shown in the figure, a detector section C3corresponds to the temperature sensors 302, 303, 402, 403, 405, pressuredetection means for detecting pressure, flow rate detection means fordetecting flow rate, voltage□current detection means for detectingvoltage□current or frequency detection means for detecting frequency,each means being not shown in the figure.

An electrically-driven expansion valve driving section C4, indoor heatexchanger driving section C5, outdoor heat exchanger driving section C6and compressor driving section C7 are means to function when a controlprogram according to each embodiment mentioned later is carried out.Each driving section mentioned above is a driver shown in FIG. 63.

The electrically-driven expansion valve driving section C4 outputscontrol signals to an electrically-driven expansion valve drive source(e.g. stepping motor) 404 and controls an opening ratio of a throttle ofthe electrically-driven expansion valve 10A through theelectrically-driven expansion valve drive source 404. The indoor heatexchanger driving section C5 outputs control signals to an indoor heatexchanger drive source (e.g. fan motor) 301 that drives the cross flowfan 91A so as to operate or halt it in response to the control signaland controls a heat exchange capacity of the indoor heat exchanger 9A bythe number of revolution. The outdoor heat exchanger driving section C6outputs control signals to an outdoor heat exchanger drive source (e.g.fan motor) 401 that drives the cross flow fan 91B so as to operate orhalt it in response to the control signal and controls a heat exchangecapacity of the outdoor heat exchanger 9B by the number of revolution.The compressor driving section C7 outputs control signals to acompressor power source (e.g. inverter module or motor) 450 thatcontrols the compressor 4 for a normal rotation, inverse rotation,start, halt and selection of its capacity. The compressor power source450 is not limited to a motor and may be an engine.

Thus, in the refrigerating cycle A, an opening of the throttle of theelectrically-driven expansion valve 10A is controlled, thereby a flowrate and a rate of change in a flow rate in the refrigerating cycle A iscontrolled. The indoor heat exchanger 9A and the outdoor heat exchanger9B are driven or halted and heat exchange capacity thereof iscontrolled, thereby a pressure of the refrigerant in the indoor heatexchanger 9A, the outdoor heat exchanger 9B and the refrigerating cycleA is controlled. A normal rotation, inverse rotation, start, halt andselection of its capacity of the compressor 4 are controlled, thereby apressure and a rate of change in a pressure of the refrigerant, and aflow rate and a rate of change in a flow rate of the refrigerant in therefrigerating cycle A are controlled. Consequently, a physical quantitysuch as a pressure, differential pressure and flow rate, and a rate ofchange in a physical quantity such as a rate of change in pressure, rateof change in differential pressure and rate of change in flow rate inthe channel selector valve 100 in the refrigerating cycle A arecontrolled. Accordingly, in each embodiment of a channel selector valvementioned later, non-electrical motive power is generated due to thephysical quantity or the rate of change in the physical quantitymentioned above, then a channel is changed by the channel selector valve100.

The control device C controls a functional component such as theelectrically-driven expansion valve 10A, indoor heat exchanger 9A,outdoor heat exchanger 9B and compressor 4 in order to generatenon-electrical motive power on the basis of a physical quantityconcerning an operation control of the refrigerating cycle such as apressure, temperature, flow rate, voltage, current, electric frequencyand mechanical oscillation frequency. The refrigerating cycle is notlimited to a heat pump-type air-conditioner and may be a heat pump-typechiller unit, engine drive-type or car air-conditioner.

FIG. 65 is a block diagram illustrating a flow of signal and actionaccording to an embodiment of a device for controlling a refrigeratingcycle of the present invention, in which an instruction for a heating orcooling operation by the remote control 500 and so on, or a demand forchange of a channel by the channel selector valve through a change ofthe operation mode is inputted in the control section C. Then, as afirst step, the control section C outputs signals with respect to“control of the compressor”, “control of the heat exchanger” or “controlof the throttle device”. Then, as a result of various controls mentionedabove, as a second step, a state of the physical quantity or the rate ofchange in the physical quantity of the refrigerating cycle changes,thereby, as a third step, a selector operation is carried out in achannel selector valve 100 according to each embodiment described later.The electrically-driven expansion valve 10A is an example of thethrottle device.

Thus, in the present invention, an electric conduction to anelectromagnetic coil by e.g. a relay contact or a semiconductor-typeswitch is not employed in order to select a channel by the channelselector valve.

In the following, some actual examples of control operationcorresponding to the channel selector valve 100 or 50 according to theembodiment mentioned above will be explained.

In the following, a control operation of the control device C thatcontrols the channel selector valve according to the first embodimentwill be explained with reference to a flow chart. The processing sectionC1 of the control device C performs a control action by themicrocomputer 330 of the indoor control section 300 and themicrocomputer 470 of the outdoor control section 400. Thesemicrocomputers 330 and 470 in cooperation perform a controlcorresponding to each flow chart explained below with performing atransfer of data by a serial communication.

FIGS. 66 and 67 are a part of a flow chart of a main routine, which iscommon as to the channel selector valve according to each embodimentfrom the first to twenty second embodiment. In the main routine, apower-on reset at a first priority level sets a first start, then atstep S11 “initialization processing—1” such as a whole clear of RAM isperformed so as to proceed to step S23. A second priority level by areset of a watchdog timer or a calling off of a wait sets a secondstart, then “initialization processing—2” such as a partial clear of RAMis performed to proceed to step S13.

At step S13, an initialization processing of the control device isperformed, then at step S14 an input processing of an operationinstruction, which inputs operation signals by the remote control 500 ora switch, is performed, then at step S15 an input processing, whichinputs a physical quantity concerning an operation control of therefrigerating cycle such as a pressure, temperature, flow rate, voltage,current, electric frequency and mechanical oscillation frequency isperformed, and then at step S16 a general processing, which performscomputation, comparison, judgement, determination of a control conditionof the refrigerating cycle and so on, is performed so as to proceed tostep S17.

At step S17, it is judged whether a data is normal or abnormal as aresult of the processing. If abnormal, in step S18 it is judged whethera degree of the abnormality requires a standby or not, then if required,the standby is set, and if not required, an operation of therefrigerating cycle is halted at step S19, then the system proceeds tostep S101 in FIG. 67. At step S101, it is judged whether the command is“select channel” or not, then if so, the system proceeds to step S102,and if not so, the system proceeds to step S105. At step S102 theoperation is set standby for a third predetermined period of time (about30 seconds), at step S103 an operation of the compressor 4 is startedwith a second predetermined capacity (e.g. 10 Hz), and at step S104 theposition data is set to be the first position after a firstpredetermined period of time (about 10 seconds), then the systemproceeds to step S108. At step 108, an operation of the refrigeratingcycle is halted, then the system proceeds to step S109 in FIG. 66. Atstep S109, the system is on standby for a predetermined period of timeuntil restart, then comes back to step S14.

On the other hand, if a data is normal at step S17, it is judged whetheran operation of the refrigerating cycle is to be started or not, and ifnot, the system comes back to step S14, and if to be started, the systemproceeds to step S111. At step S111, by each sub routine mentionedlater, a drive processing of the functional component such as thecompressor, electrically-driven expansion valve and heat exchange motorin response to each embodiment and a detection processing for detectinga position of the movable member (e.g. the piston cylinder 12) of thechannel selector valve are performed, thereby a control of selection ofthe channel selector valve according to each embodiment is carried out.

At step S112, it is judged whether a position data of the movable memberof the channel selector valve coincides with a command data or not, thenif not, the system proceeds to step S19, and if coincides, variousoutput processing such as a display is performed at step S113, then thesystem proceeds to step S114. At step S114, it is judged whether anoperation of the refrigerating cycle is to be continued or not, then ifnot, the system proceeds to step S19, and if to be continued, at stepS115 it is judged whether the command is “select channel” or not. Ifnot, the system comes back to step S14, while if so, the system performsa processing of an operation or halt of the compressor in response toeach embodiment at step S116, then comes back to step S14.

FIG. 68 is a flow chart of a sub-routine (step S111) for a channelselector valve (FIGS. 1 and 2) according to the first embodiment of thepresent invention. At step S21, it is watched whether an operation ofthe refrigerating cycle is to be started or not, and if to be started,it is judged whether the command is “select channel” or not at step S22.If not, an operation of the compressor 4 is started with a secondpredetermined capacity (e.g. 10 Hz), then the system proceeds to stepS26, while if the command is “select channel”, a processing fortransferring the liquid refrigerant in FIG. 69 is performed at step S24,then an operation of the compressor 4 is started with a firstpredetermined capacity (e.g. 30 Hz) at step S25 and then, the systemproceeds to step S26. Here, the step S23 corresponds to claim 87 and thestep S25 corresponds to claim 76.

At step S26 a drive processing (normal processing) of the throttledevice is performed, at step S27 a drive processing (normal processing)of the heat exchanger motor is performed, and at step S28 a detectionprocessing of a position of the channel selector valve is performed,thereby the system comes back to a main routine. In this detectionprocessing of a position of the channel selector valve, a state of achannel in the channel selector valve, i.e. a position of the movablemember is detected by comparing a temperature Tc of the indoor heatexchanger 9A with a temperature Tc′ of the outdoor heat exchanger 9B.The state of a channel in the channel selector valve may be detected bycomparing a pressure of the indoor heat exchanger 9A with a pressure ofthe outdoor heat exchanger 9B. When a slide valve 27 of the channelselector valve moves, there is a short cycle mode (a phenomenon that ahigh pressure side is connected to a low pressure side) even though itappears in a short period of time. At this time, there is a load changeof the compressor 4, which appears as a fluctuation in a load current.Therefore, such a method may be employed that a state of selection ofthe channel selector valve is detected by watching the load current whenthe command “select channel” by the channel selector valve is set. Forthis purpose, the load current is watched by detecting a voltage betweenboth ends of a shunt resistor shown in FIG. 64.

A processing for transferring a liquid refrigerant shown in FIG. 69corresponds to claim 77. At step S241 an operation of the compressor 4is started with a second predetermined capacity (e.g. 10 Hz), at stepS242 an operation of the refrigerating cycle is performed for a fourthpredetermined period of time (equal to or longer than about threeminutes), and at step S243 an operation of the refrigerating cycle ishalted for a fifth predetermined period of time (shorter than aboutthree minutes), then the system comes back to the former routine. Thisprocessing for transferring a liquid refrigerant may be omitted,although the movable member easily moves, if this processing isincluded.

In the processing of an operation or halt of the compressor at step S116of the main routine, the compressor 4 is operated with a thirdpredetermined capacity (e.g. 5 Hz) in the first embodiment and thesystem comes back to step S14, which corresponds to claim 83.

With the processings described above, when a channel is not switched bythe channel selector valve, the movable member is held at the firstposition at step S23, while when a channel is switched, the movablemember is moved from the first position to the second position at stepS25.

If a connection relationship between the pipes 7 and 8 and heatexchangers 9A and 9B in the first embodiment is reversed, a control ofthe system can be performed in such a manner that the piston cylinder 12is situated at the second position in the heating mode and that thepiston cylinder 12 is situated at the first position in the coolingmode.

FIG. 70 is a flow chart of a sub-routine (step S111 in FIG. 66) for achannel selector valve (FIGS. 9 to 14) according to the fifth embodimentof the present invention. At step S31 it is watched whether an operationof the refrigerating cycle is to be started or not, and if to bestarted, it is judged whether the command is “select channel” or not atstep S32. If the command is not “select channel”, it is judged whetherthe position data is the first position or not, and if not the firstposition, the system proceeds to step S38, while if the first position,an operation of the compressor 4 is started with a first predeterminedcapacity (e.g. 30 Hz) at step S34 and the position data is renewed tothe second position after a first predetermined period of time (e.g.about 10 seconds) at step S35. Then, at step S36 an operation of therefrigerating cycle is halted, at step S37 the operation is set standbyfor a third predetermined period of time (about 30 seconds) and then,the system proceeds to step S38. At step S38 an operation of thecompressor 4 is started with a second predetermined capacity (e.g. 10Hz), at step S39 the compressor 4 is operated with a predeterminedcapacity (corresponding to a load) after a first predetermined period oftime (about 10 seconds) and then, the system proceeds to step S308.

On the other hand, if the command is “select channel” at step S32, it isjudged whether the position data is the second position or not at stepS301, and if not the second position, the system proceeds to step S306,while if the second position, an operation of the compressor 4 isstarted with a second predetermined capacity (e.g. 10 Hz) at step S302,then the position data is renewed to the first position after a firstpredetermined period of time (about 10 seconds) at step S303. Then, atstep S304 an operation of the refrigerating cycle is halted, at stepS305 the operation is set standby for a third predetermined period oftime (about 30 seconds), and the system proceeds to step S306. At stepS306 an operation of the compressor 4 is started with a firstpredetermined capacity (e.g. 30 Hz), at step S307 the compressor 4 isoperated with a predetermined capacity (corresponding to a load) after afirst predetermined period of time (about 10 seconds), then the systemproceeds to step S308.

At step S308 a drive processing (normal processing) of the throttledevice is performed, at step S309 a drive processing (normal processing)of the heat exchanger motor is performed, and at step S310 a detectionprocessing of a position of the channel selector valve is performedsimilarly to the step S28, then the system comes back to the mainroutine (FIG. 66). The steps S34 to S37 and S302 to S305 correspond toclaim 74.

In the processing of an operation or halt of the compressor at step S116of the main routine, a processing to halt an operation of the compressor4 is performed in the fifth embodiment and following each embodimentstarting with the ninth embodiment, and then the system comes back tostep S14, which corresponds to claim 83.

In the channel selector valve according to the fifth embodiment, if aconnection relationship between the pipes 7 and 8 and heat exchangers 9Aand 9B is reversed, a position of selection of a channel is reversed inresponse to the operation mode.

A processing to perform a control of selection of the channel selectorvalve according to the thirteenth embodiment and the channel selectorvalve 51 according to the fifteenth embodiment is similar to a controlof the channel selector valve according to the fifth embodiment shown inFIG. 70, in which the channel selector valve 51 is controlled bycontrolling an operation of the compressor 4.

FIG. 71 is a flow chart of a sub-routine (step S111 in FIG. 66) for achannel selector valve (FIGS. 24 to 27) according to the ninthembodiment of the present invention. At step S41 it is watched whetheran operation of the refrigerating cycle is to be started or not, and ifto be started, it is judged whether the command is “select channel” ornot at step S42. If the command is not “select channel”, an openingratio of the electrically-driven expansion valve is set almost fullyclosed, at step S44 an operation of the compressor 4 is started with asecond predetermined capacity (e.g. 10 Hz), at step S45 the openingratio of the electrically-driven expansion valve is set back to apredetermined opening ratio (corresponding to a load) after a firstpredetermined period of time (about 10 seconds), then the systemproceeds to step S49.

On the other hand, if the command is “select channel” at step S42, theopening ratio of the electrically-driven expansion valve is set almostfully opened at step S46, an operation of the compressor 4 is startedwith a first predetermined capacity (e.g. 30 Hz) at step S47, theopening ratio of the electrically-driven expansion valve is set back toa predetermined opening ratio (corresponding to a load) after a firstpredetermined period of time (about 10 seconds) at step S48, then thesystem proceeds to step S49.

At step S49 a drive processing (normal processing) of the throttledevice is performed, and at step S401 a detection processing of aposition of the channel selector valve is performed similarly to thestep S28, then the system comes back to the main routine (FIG. 66). Thesteps S43 and S46 correspond to claim 78, while the step S48 correspondsto claim 81.

In FIGS. 24 and 25, the capillary tube 10B is provided between thechannel 14A and the indoor heat exchanger 9A and the electrically-drivenexpansion valve 10A is provided between the channel 14A and the outdoorheat exchanger 9B. Instead, positions of the capillary tube 10B and theelectrically-driven expansion valve 10A can be changed with each other.In this case, a control can be performed by replaceing steps S42, S43and S46 in a flow chart shown in FIG. 71 with steps S42′, S43′ and S46′in a flow chart shown in FIG. 72. That is, if the command is not “selectchannel” at step S42′, an opening ratio of the electrically-drivenexpansion valve is set almost fully opened at step S43′, then the systemproceeds to step S44, while if the command is “select channel” at stepS42′, an opening ratio of the electrically-driven expansion valve is setalmost fully closed at step S46′, then the system proceeds to step S47.

FIG. 73 is a flow chart of a sub-routine (step S111 in FIG. 66) for achannel selector valve according to the tenth embodiment (FIGS. 28 and29) of the present invention. At step S51 it is watched whether anoperation of the refrigerating cycle is to be started or not, and if tobe operated, it is judged whether the command is “select channel” or notat step S52. If the command is not to switch a channel, at step S53 anoperation of the compressor 4 is started with a second predeterminedcapacity (e.g. 10 Hz), at step S54 a drive processing (normalprocessing) of the electrically-driven expansion valve is performed, atstep S55 a drive processing (normal processing) of the heat exchangermotor is performed, and at step S56 the compressor 4 is operated with apredetermined capacity (corresponding to a load) after a firstpredetermined period of time (about 10 seconds), then the systemproceeds to step S502.

On the other hand, if the command is “select channel” at step S52, anoperation of the compressor 4 is started at step S57 and driven at aspecific frequency. Then, at step S58 a drive processing (normalprocessing) of the throttle device is performed, at step S59 a driveprocessing (normal processing) of the heat exchanger motor is performed,and at step S501 the compressor 4 is operated with a predeterminedcapacity (corresponding to a load) after a first predetermined period oftime (about 10 seconds), then the system proceeds to step S502.

At step S502 a detection processing of a position of the channelselector valve is performed similarly to the step S28, then the systemcomes back to the main routine (FIG. 66). The step S57 corresponds toclaim 75 and the step S501 corresponds to claim 80.

With the processings mentioned above, a control of selection of thechannel selector valve is carried out by resonating the pilotoscillation valve 30 with the compressor 4.

FIG. 74 is a flow chart of a sub-routine (step S111 in FIG. 66) for achannel selector valve according to the eleventh embodiment (FIGS. 30and 31) of the present invention. At step S61 it is watched whether anoperation of the refrigerating cycle is to be started or not, and if tobe started, it is judged whether the command is “select channel” or notat step S62. If the command is not “select channel”, at step S63 a driveprocessing (normal processing) of the heat exchanger motor is performed,at step S64 an operation of the compressor 4 is started with a secondpredetermined capacity (e.g. 10 Hz), at step S65 the compressor 4 isoperated with a predetermined capacity (corresponding to a load) after afirst predetermined period of time (about 10 seconds), and at step S66 adrive processing (normal processing) of the throttle device isperformed, then the system proceeds to step S603.

On the other hand, if the command is “select channel” at step S62, atstep S67 an operation of the heat exchanger motor is kept halted, atstep S68 an operation of the compressor 4 is started with a firstpredetermined capacity (e.g. 30 Hz), and at step S69 an operation of theheat exchanger motor is started after a second predetermined period oftime (about 20 seconds), then an operation of the heat exchanger motoris started. Then, at step S601 the compressor 4 is operated with acapacity required to hold the movable member (e.g. the piston cylinder12) at the second position, and at step S602 a drive processing (normalprocessing) of the throttle device is performed, then the systemproceeds to step S603. At step S603 a detection processing of a positionof the channel selector valve is performed similarly to the step S28,then the system comes back to the main routine (FIG. 66). The step 67corresponds to claim 79 and the steps S69 and S601 correspond to claim82.

With the processings mentioned above, a control of selection of thechannel selector valve is carried out by controlling the heat exchanger.

In the first to eleventh embodiments mentioned above, the channelselector valve constructed by employing a slide-type four-way selectorvalve is explained. In the following, an embodiment, in which thepresent invention is applied to a rotary channel selector valve thatperforms its channel selector operation by rotation of a main valveelement in a valve housing will be explained.

A schematic constitution of a refrigerating cycle A employing a rotarychannel selector valve will be explained with reference to FIG. 35, inwhich the same abbreviation numerals with those used for thecorresponding identical members or parts of the refrigerating cycle Ashown in FIG. 63 are used.

In FIG. 35, a channel of the refrigerant in the cooling mode is shown bysolid lines while that in the heating mode is shown by broken lines. Inthis refrigerating cycle A, a place where the high pressure refrigerantdischarged from the compressor 4 is guided to and a place where therefrigerant to be sucked by the compressor 4 by way of an accumulator200 is guided from are mutually selected out of the indoor heatexchanger 9A and the outdoor heat exchanger 9B by a rotary four-wayselector valve 50, and an electrically-driven expansion valve 10A isprovided between the indoor heat exchanger 9A and the outdoor heatexchanger 9B. Pressure sensors Pc and Pc′ are disposed at the indoorheat exchanger 9A and the outdoor heat exchanger 9B, respectively, todetect each pressure, thereby a position of the movable member can bedetected. These pressure sensors may be disposed at a channel near therotary four-way selector valve 50.

FIG. 75 is a flow chart of a sub-routine (step S111 in FIG. 66) for achannel selector valve 81 according to the eighteen embodiment of thepresent invention. At step S71 a judge processing of an operationcommand by a microcomputer is performed, and at step S72 it is judgedwhether an operation mode required is the cooling mode or not. If thecooling mode is required, processings starting from step S73 areperformed, on the other hand if the heating mode is required,processings starting from step S703 are performed.

At step S73 it is judged whether a position data is the first positionor not, and if not, the system proceeds to step S78, on the other handif the first position, at step S74 an operation of the compressor 4 isstarted in its inverse direction, then at step S75 the position data isrenewed into the second position after a first predetermined period oftime (e.g. 10 seconds). Then, at step S76 an operation of therefrigerating cycle is halted, an at step S77 an operation thereof isset standby for a third predetermined period of time (about 30 seconds),then the system proceeds to step S78. At step S78 an operation of thecompressor 4 is started with a first predetermined capacity (e.g. 30Hz), then at step S79 the compressor 4 is operated with a predeterminedcapacity (corresponding to a load) after a first predetermined period oftime (e.g. 10 seconds). Then, at step S701 it is watched whether thereis an indication of halt of an operation (cooling operation) or not, andif there is, at step S702, an operation of the compressor 4 is haltedand the system is set standby for a third predetermined period of time(about 30 seconds) with keeping the position data to be the secondposition, then the system comes back to the former routine.

On the other hand, at step S72 if the heating mode is required, at stepS703 it is judged whether a position data is the second position or not,and if not, the system proceeds to step S708, on the other hand if thesecond position, at step S704 an operation of the compressor 4 isstarted in its inverse direction, then at step S705 the position data isrenewed into the first position after a first predetermined period oftime (e.g. 10 seconds). Then, at step S706 an operation of therefrigerating cycle is halted, an at step S707 an operation thereof isset standby for a third predetermined period of time (about 30 seconds),then the system proceeds to step S708. At step S708 an operation of thecompressor 4 is started with a first predetermined capacity (e.g. 30Hz), then at step S709 the compressor 4 is operated with a predeterminedcapacity (corresponding to a load) after a first predetermined period oftime (e.g. 10 seconds). Then, at step S710 it is watched whether thereis an indication of halt of an operation (heating operation) or not, andif there is, at step S711, an operation of the compressor 4 is haltedand the system is set standby for a third predetermined period of time(about 30 seconds) with keeping the position data to be the firstposition, then the system comes back to the former routine.

INDUSTRIAL APPLICABILITY

According to a channel selector valve of the present invention since achannel selection of fluid by the channel selector valve is performed byemploying non-electric motive power generated when a control sectioncontrols a physical quantity of the fluid, there is no necessity ofusing an electrically-driven drive source such as an electromagneticsolenoid, resulting in decreasing cause of fault to occur, improving areliability of the operation, contributing to prevention ofenvironmental pollution due to an operation at a power plant andpowerful promotion of energy saving and the like.

According to the channel selector valve of the present invention asdescribed above, a channel selection of fluid by the channel selectorvalve is passively performed using motive power generated by anon-electrically-driven drive source provided separately from thechannel selector valve, therefore there is no necessity for the channelselector valve to have a source for generating motive power.

According to the channel selector valve of the present invention asdescribed above, at least one of element components in a refrigeratingcycle having the channel selector valve is used as the drive source,therefore there is no necessity to newly provide a drive source forselecting a channel by a channel selector valve.

According to the channel selector valve of the present invention asdescribed above, the element component in the refrigerating cycle actsso that a change in a physical quantity is generated in therefrigerating cycle, therefore a selection of a channel of fluid by thechannel selector valve is performed as a consequence.

According to the channel selector valve of the present invention asdescribed above, at least one change among changes in pressure,differential pressure and flow rate of fluid in the channel selectorvalve arising from an action of the element component in therefrigerating cycle is used, therefore a selection of a channel by thechannel selector valve can be easily performed by using such a change inphysical quantity generated in the refrigerating cycle as motive power.

According to a channel selector valve of the present invention asdescribed above, a selection of a place where a main port iscommunicated to between two selector ports, which is achieved by movinga movable member between the first and second positions, can beperformed without using electric motive power, resulting in decreasingcause of fault to occur. Therefore, there is no necessity of a drivesource to generate electric motive power, resulting in decreasing causeof fault to occur, improving a reliability of the operation,contributing to prevention of environmental pollution due to anoperation at a power plant and powerful promotion of energy saving andthe like.

According to the channel selector valve of the present invention asdescribed above, the element component in the refrigerating cycle actsso that a change in a physical quantity is generated in therefrigerating cycle, therefore a selection of a channel of fluid by thechannel selector valve is performed as a consequence without a drivesource newly provided.

According to the channel selector valve of the present invention asdescribed above, at least one change among changes in pressure,differential pressure and flow rate of fluid in the channel selectorvalve arising from an action of the element component in therefrigerating cycle is used, therefore a selection of a channel by thechannel selector valve can be easily performed by using such a change inphysical quantity generated in the refrigerating cycle as motive power.

According to a channel selector valve of the present invention asdescribed above, first and second three-way selector valves constitutedby the channel selector valve are combined, therefore a four-wayselector valve, which can select a channel of fluid, is easilyconstructed without using electric motive power by a simple combinationof valves usable separately.

According to the channel selector valve of the present invention asdescribed above, an action of a first three-way selector valve isincorporated with that of a second three-way selector valve so that thechannel selector valve functions securely as a four-way selector valveby the combination.

According to the channel selector valve of the present invention asdescribed above, the movable member of the first three-way selectorvalve situated at the first position is moved to the second position bya first drive mechanism of the first three-way selector valve, while themovable member of the first three-way selector valve situated at thesecond position is moved to the first position by a second drivemechanism, a pressure of fluid at the first selector port is set equalto that at the second selector port, thereby a movement of the movablemember of the second three-way selector valve is passively performed.

According to the channel selector valve of the present invention asdescribed above, a pressure of fluid at the main port is suitablyadjusted in response to a position of the movable member of the firstthree-way selector valve, and an energizing force to move the movablemember of the first three-way selector valve to a different position isstored in storing means for storing energizing force, the movable memberof the first three-way selector valve is moved by the energizing forcewithout using electric motive power, thereby the movable member of thesecond three-way selector valve can be passively moved without usingelectric motive power.

According to the channel selector valve of the present invention asdescribed above, by using a channel selector valve that solelyconstructs a four-way selector valve, a place where fluid introducedfrom the exterior of the housing flows to and a place where fluiddischarged to the exterior of the housing is introduced from can beselected without using electric motive power.

According to the channel selector valve of the present invention asdescribed above, the movable member can be moved without using electricmotive power due to a difference between a pressure of fluid introducedfrom the exterior of the housing and a pressure of fluid discharged tothe exterior of the housing, which is generated between the first spaceof the first pressure chamber partitioned by the movable member in thehousing and the second pressure chamber, thereby a channel of fluid canbe selected.

According to a method of driving the channel selector valve of thepresent invention as described above, when the channel selector valve isdriven, even if there is no difference between a pressure of fluid inthe first space and a pressure of fluid in the second pressure chamber,the movable member can be moved from the second position to the firstposition by an energizing force of the energizing means, and adifference between a pressure of fluid in the first space and a pressureof fluid in the second pressure chamber is set in response to theenergizing force of the energizing means so that the movable member isheld at the first or second position, thereby a selection state of achannel of fluid can be maintained.

According to the channel selector valve of the present invention asdescribed above, the movable member easily can be kept being situated atthe first or second position by making use of a static friction forcebetween the valve seat and the movable member.

According to a method of driving the channel selector valve of thepresent invention as described above, when the channel selector valve isdriven, a selection of a channel of fluid that is achieved by moving themovable member from the first position to the second position is carriedout by using a change in pressure of fluid in the first space withoutusing electric motive power generated by an electrically-driven drivesource such as an electromagnetic solenoid and the like, thereafter aselection state, in which the movable member is situated at the secondposition, can be maintained.

According to the channel selector valve of the present invention asdescribed above, the movable member can be moved between the first andsecond positions by making use of an internal pressure of the housing,which is changed by fluid introduced from the exterior into the interiorof the housing by way of an inlet port of the housing, without usingelectric motive power generated by an electrically-driven drive sourcesuch as an electromagnetic solenoid and the like.

According to the channel selector valve of the present invention asdescribed above, a selector valve element of a non-electrically-drivenpilot valve is moved between a fifth position and a sixth position,thereby a place in which a pressure of fluid is lower than that in thefirst space of the first pressure chamber is selected between the secondpressure chamber and the third pressure chamber, which are partitionedby the movable member and situated sandwiching the first pressurechamber therebetween, the movable member is moved by a motive power aslow as a power required to perform a selection of the selector valveelement of the pilot valve, and a selection of a channel of fluid can becarried out.

According to the channel selector valve of the present invention asdescribed above, when a difference between a pressure of fluid in thesecond pressure chamber and that in the third pressure chamber cancelsout, the selector valve element is moved from one to another between thefifth and sixth positions by second driving means, thereby the movablemember can be moved from one to another between the first and secondpositions without using electric motive power.

According to the channel selector valve of the present invention asdescribed above, a difference in a pressure of fluid is generatedbetween a fourth pressure chamber and a fifth pressure chamber of thepilot valve with making these chambers be communicated to or isolatedwith the second or third pressure chamber, by using a first or secondsubvalve in response to a movement of the movable member, and anenergizing force is suitably stored to third or fourth storing means forstoring energizing force, thereby a movement of the selector valveelement in the pilot valve over a range from a fifth position to aneighth position, which is for generating a difference in a pressure offluid between the third and second pressure chambers, said differencebeing transformed into a motive power to move the movable member, can beperformed without using electric motive power.

According to the channel selector valve of the present invention asdescribed above, when a difference between a pressure of fluid in thesecond pressure chamber and that in the third pressure chamber cancelsout, the selector valve element is moved from one to another between thefifth and sixth positions by second driving means, thereby the movablemember can be moved from one to another between the first and secondpositions without using electric motive power.

According to the channel selector valve of the present invention asdescribed above, an energizing force is suitably stored to third orfourth storing means for storing energizing force of the pilot valve byusing a difference in a pressure of fluid generated between a secondpressure chamber and a third pressure chamber, thereby the selectorvalve element is moved to a seventh or eighth position when a differencebetween a pressure of fluid in the second pressure chamber and that inthe third pressure chamber cancels out, thereby making a change in adifference in pressure between fluid in a fourth pressure chamber of thepilot valve, which communicates with the third pressure chamber, andfluid in a fifth pressure chamber of the pilot valve, which communicateswith the second pressure chamber, thereby the movable member can bemoved from one to another between the first and second positions withoutusing electric motive power.

According to the channel selector valve of the present invention asdescribed above, the movable member is moved from one to another betweenthe first and second positions by changing a pressure of fluidintroduced from the exterior to the interior of the housing by way of aninlet port of the housing, while the movable member is moved fromanother to one between the first and second positions only orsupplementarily by using an energizing force stored in the energizingmeans, thereby a selection of a channel by the channel selector valvecan be easily and securely achieved without using electric motive power.

According to the channel selector valve of the present invention asdescribed above, the movable member situated at either the first orsecond position is stayed at one position or moved to another positionselectively, thereby a selection of a channel by the channel selectorvalve can be securely achieved without using electric motive power.

According to the channel selector valve of the present invention asdescribed above, the latch mechanism selectively performs the first orsecond state, thereby a selection of a channel by the channel selectorvalve can be securely achieved without using electric motive power.

According to the channel selector valve of the present invention asdescribed above, a selection of a channel by the channel selector valvecan be achieved without directly affecting a large impact to the movablemember, that is, without directly applying a control to a movement ofthe movable member.

According to a method of driving the channel selector valve of thepresent invention as described above, after a control of a movement ofthe movable member situated at one position by the latch mechanism isremoved, the movable member can be securely moved from the one positionto another position, in addition, the latch mechanism can control amovement of the movable member, that is, securely control the movablemember to be situated at the one position.

According to the channel selector valve of the present invention asdescribed above, when the second latch mechanism controls a movement ofa valve-opening member, the movable member, which is moved from oneposition to another position by the third drive mechanism, can move fromthe another position to the one position by the fourth drive mechanism,while to the contrary, when the second latch mechanism does not controla movement of a valve-opening member, the movable member, which is movedfrom one position to another position by the third drive mechanism, canbe held at the another position by using a motive power of the thirddrive mechanism without using an exclusive drive source and the like.

According to the channel selector valve of the present invention asdescribed above, a state, in which the movable member moved from oneposition to another position by the third drive mechanism is held at theanother position, can be mutually produced whenever the third drivemechanism generates a motive power.

According to a method of driving the channel selector valve of thepresent invention as described above, the second latch mechanism istransferred between a state in which a movement of the valve-openingmember from the valve-closing position to the valve-opening position iscontrolled and a state in which said control is removed, thereby thesystem can be transferred from one state, in which the movable membercan move from the another position to the one position by using a motivepower generated by the fourth drive mechanism, to another state in whichthe movable member cannot move from the another position to the oneposition, or the system can be transferred from the another state to theone state.

According to the channel selector valve of the present invention asdescribed above, a selection, which is achieved by moving the movablemember between the first and second positions, of a place to which thefluid introduced from the exterior of the housing into the first spaceby way of the inlet port is discharged and a place from which the fluiddischarged from the second space to the exterior of the housing by wayof the outlet port is introduced, is carried out by a change in pressureof the fluid introduced into the first space without using an exclusivedrive source such as an electromagnetic solenoid.

According to the channel selector valve of the present invention asdescribed above, the movable member moved from the first position to thesecond position by using a motive power generated by anon-electrically-driven drive source can be held at the second positioneven if the motive power is not continuously supplied.

According to the channel selector valve of the present invention asdescribed above, a force applied to the movable member is adjusted byfluid in the first space, thereby a selection of a channel by thechannel selector valve can be securely achieved without using anelectrically-driven drive source.

According to the channel selector valve of the present invention asdescribed above, a force applied to the movable member is adjusted byfluid in the first space, thereby a selection of a channel by thechannel selector valve can be securely achieved without using anelectrically-driven drive source, in addition, even if a force appliedto the movable member by a pressure of fluid in the first space becomesequal to a force applied to the movable member by a pressure of fluid inthe second space, an energizing force of the energizing means moves themovable member to the first position, thereby the first position can beset as an initial position of the movable member.

According to a method of driving the channel selector valve of thepresent invention as described above, when the channel selector valve isdriven, a force applied to the movable member in a direction from thefirst to second position is set to exceed a force applied to the movablemember in a direction from the second to first position, thereby themovable member is moved from the first position to the second position,then the force applied to the movable member in a direction from thefirst to second position can be lowered as long as said forcecorresponds to a pressure to hold the movable member at the secondposition, therefore a degree of freedom in an operation of therefrigerating cycle can be raised after the movable member is moved tothe second position.

According to the channel selector valve of the present invention asdescribed above, an opening ratio of the electrically-driven expansionvalve is changed to change a pressure of fluid, thereby the movablemember easily moves between the first and second positions and aselection of a channel by the channel selector valve can be securelyachieved without using electric motive power.

According to the channel selector valve of the present invention asdescribed above, a frequency of an oscillation generated by thecompressor is changed, thereby the movable member easily moves betweenthe first and second positions and a selection of a channel by thechannel selector valve can be securely achieved without using electricmotive power.

According to the channel selector valve of the present invention asdescribed above, a difference in fluid pressure is changed, for example,by changing an efficiency of heat exchange by the heat exchanger,thereby the movable member easily moves between the first and secondpositions and a selection of a channel by the channel selector valve canbe securely achieved without using electric motive power.

According to the channel selector valve of the present invention asdescribed above, a space required for the movable member to move betweenthe first and second positions can be set smaller than that in a case ofa linear slide-type channel selector valve. Also, the main valve elementis moved by using a difference between a pressure of fluid introducedfrom the exterior of the housing and that of fluid discharged to theexterior of the housing, which is generated between the second pressurechamber and the first space in the first pressure chamber partitioned bythe main valve element, thereby a channel of fluid can be selected.

According to the channel selector valve of the present invention asdescribed above, a pressure of fluid, which flows into secondcommunication means formed at one end surface of the main valve elementfor communicating the ports of the valve seat with each other, isutilized so as to generate a rotative thrust of the main valve element,thereby the main valve element can be rotated without using electricmotive power and a channel of fluid can be selected.

According to the channel selector valve of the present invention asdescribed above, a fluid in the inlet port and a fluid in the outletport, which are formed at a reverse side of the housing with each other,generate a difference in pressure of the fluid between both sides of thehousing sandwiching the main valve element, and by utilizing thisdifference in pressure the main valve element can be rotated between thefirst and second positions without using electric motive power.

According to the channel selector valve of the present invention asdescribed above, the main valve element is moved in a direction of thecentral axis of the housing by using non-electric motive power so as totransform this movement in a direction of the central axis into arotation in a direction of circumference of the housing by theconversion means of moving direction, thereby the main valve element isrotated between the first and second positions and a channel of fluidcan be selected.

According to the channel selector valve of the present invention asdescribed above, a movement of the cam follower pin in the cam groovetransforms a movement of the main valve element in a direction of thecentral axis by using non-electric motive power into a rotation in adirection of circumference of the housing, thereby a channel of fluidcan be selected without using electric motive power.

According to the channel selector valve of the present invention asdescribed above, when a cam groove is formed in the housing, a guide ofthe first half of the inner housing is joined with a guide of the secondhalf of the inner housing, thereby the cam follower pin of the mainvalve element disposed in the housing can be easily disposed in the camgroove.

According to the channel selector valve of the present invention asdescribed above, the end surface of the main valve element, on which thesecond communication means is formed for communicating the ports of thevalve seat with each other, is away from the valve seat at a positionexcept the first and second positions where the ports can communicateswith each other by the second communication means, thereby anequalization of a pressure of the fluid in each port, in a state thatthe ports cannot communicate with each other, can be easily achievedwithout using electric motive power.

According to the channel selector valve of the present invention asdescribed above, when the main valve element is situated at a positionexcept the first and second positions, where the main valve element isaway from the valve seat so that the ports cannot communicate with eachother by the second communication means, a communication channel, whichselectively communicates the opposite port formed at the opposite endside of the housing to the two selector ports formed at the valve seatat the one end side of the housing, is closed by the subvalve energizedtoward a direction of closing by the subvalve energizing means, therebyan unnecessary communication between the opposite port and the selectorport, in a state that is not a normal selection state, can be preventedfrom occurring.

According to the channel selector valve of the present invention asdescribed above, a part of a movement of the main valve element toward adirection of the central axis of the housing, which is needed to rotatethe main valve element, is achieved by moving the main valve elementaway from the valve seat with an own weight of the main valve, therebynon-electric motive power required to move the main valve element can bereduced.

According to the channel selector valve of the present invention asdescribed above, a movement of the main valve element in the directionaway from the valve seat, which is needed for the movable member torotate for moving from one to another between the first and secondpositions, is performed only or supplementarily by using an energizingforce stored in the energizing means for energizing the main valveelement, thereby a selection of a channel by the channel selector valvecan be easily and securely achieved without using electric motive power.

According to the channel selector valve of the present invention asdescribed above, a movement of the main valve element in the directionnearer to the valve seat, which is needed for the movable member torotate for moving from another to one between the first and secondpositions, is performed only or supplementarily by using an energizingforce stored in the second energizing means for energizing the mainvalve element, thereby a selection of a channel by the channel selectorvalve can be easily and securely achieved without using electric motivepower.

According to the channel selector valve of the present invention asdescribed above, the main valve element is moved in the direction nearerto the valve seat or in the direction away from the valve seat by usingnon-electric motive power, thereby it is easily to set up whether themain valve element is repeatedly rotated at the same position out ofeither the first or second position or is rotated at a differentposition.

According to the channel selector valve of the present invention asdescribed above, when the cam follower pin is placed in the groove ofthe cam groove in order to situate the main valve element at oneposition out of the first and second positions, the main valve elementis prevented from rotating at another position out of the first andsecond positions upon a next rotation of the main valve element.

According to the channel selector valve of the present invention asdescribed above, when the cam follower pin is placed in the secondgroove of the cam groove in order to situate the main valve element atanother position, which is different from the former position, out ofthe first and second positions, the main valve element is prevented fromcoming back to the former position upon a next rotation of the mainvalve element.

According to the channel selector valve of the present invention asdescribed above, a movement of the main valve element in the directionnearer to or away from the valve seat, which is needed to rotate themain valve element between the first and second positions, can beperformed by smoothly rotating the main valve element between the firstand second positions with the aid of the slide means that reduces asliding resistance between the main valve element and the housing.

According to a compressor with the channel selector valve of the presentinvention as described above, a compressor, with which the channelselector valve is integrated, can be easily constructed, in addition,since there is no necessity to use a pipe for forming a high pressurechamber inside, reducing pipe laying and pipe joining around thecompressor, thereby reducing leak of fluid at the joining portion ofpipes and contributing to prevention of air pollution when the fluid issome kind of refrigerant. Moreover, since there is no current conductingpart for an electromagnetic solenoid and the like around the compressorthat generates oscillation, the above construction also prevents anoccurrence of an electrical fault due to failure in current conductionat an electric contact and a breaking of electric wire and the like,thereby reliance of the operation can be improved.

According to a device for controlling a refrigerating cycle of thepresent invention as described above, since the channel selector valveis controlled by controlling the functional components for controllingthe operation of the refrigerating cycle, upon a selector operation of avalve such as a four-way selector valve provided in the refrigeratingcycle for selecting a channel of fluid, prevention of environmentalpollution and energy saving and the like are effectively achieved.

According to a device for controlling a refrigerating cycle of thepresent invention as described above, the functional component iscontrolled to control an operation of the refrigerating cycle, therebygenerating a non-electrical motive power, by which the channel selectorvalve is passively controlled, therefore, upon a selector operation of avalve such as a four-way selector valve provided in the refrigeratingcycle for selecting a channel of fluid, prevention of environmentalpollution and energy saving and the like are effectively achieved.

According to a device for controlling a refrigerating cycle of thepresent invention as described above, by using a microcomputer, whichcontrols an operation of the refrigerating cycle, the functionalcomponent is controlled to control an operation of the refrigeratingcycle, thereby generating a non-electrical motive power, by which thechannel selector valve is passively controlled, therefore, upon aselector operation of a valve such as a four-way selector valve providedin the refrigerating cycle for selecting a channel of fluid, preventionof environmental pollution and energy saving and the like areeffectively achieved.

According to a device for controlling a refrigerating cycle of thepresent invention as described above, the functional component iscontrolled to control an operation of the refrigerating cycle, thereby aphysical quantity or a rate of change in the physical quantity isgenerated as a non-electrical motive power, by which the channelselector valve is passively controlled, therefore, upon a selectoroperation of a valve such as a four-way selector valve provided in therefrigerating cycle for selecting a channel of fluid, prevention ofenvironmental pollution and energy saving and the like are effectivelyachieved.

According to a device for controlling a refrigerating cycle of thepresent invention as described above, by using a microcomputer, whichcontrols an operation of the refrigerating cycle, the functionalcomponent is controlled to control an operation of the refrigeratingcycle, thereby a physical quantity or a rate of change in the physicalquantity is generated as a non-electrical motive power, by which thechannel selector valve is passively controlled, therefore, upon aselector operation of a valve such as a four-way selector valve providedin the refrigerating cycle for selecting a channel of fluid, preventionof environmental pollution and energy saving and the like areeffectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, in order to generate anon-electrical motive power for controlling the channel selector valve,the functional component is controlled on the basis of a physicalquantity, which concerns with a control of an operation of therefrigerating cycle, selected from the group consisting of a pressure,temperature, rate of flow, voltage, current, electrical frequency andmechanical oscillation frequency, therefore, upon a selector operationof a valve such as a four-way selector valve provided in therefrigerating cycle for selecting a channel of fluid, prevention ofenvironmental pollution and energy saving and the like are effectivelyachieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the physical quantity, which isthe non-electrical motive power and is generated by the refrigeratingcycle, is a pressure, differential pressure or rate of flow with respectto fluid existing in the channel selector valve, and the rate of changein a physical quantity, which is the non-electrical motive power and isgenerated by the refrigerating cycle, is a rate of change in pressure,rate of change in differential pressure or rate of change in rate offlow with respect to the fluid, therefore, upon a selector operation ofa valve such as a four-way selector valve provided in the refrigeratingcycle for selecting a channel of fluid, prevention of environmentalpollution and energy saving and the like are effectively achieved.

According to a device for controlling a refrigerating cycle of thepresent invention as described above, an operational condition of therefrigerating cycle is commanded from an operation command section and aphysical quantity generated by the refrigerating cycle is detected in aphysical quantity detector section, then the control section receivesinput signals sent from the operation command section and the physicalquantity detector section. Then, the control section sends outputsignals to a driving section that drives a drive source of at least oneof a plurality of functional components communicated to therefrigerating cycle so as to control said functional component, and thedevice generates a non-electrical motive power by controlling therefrigerating cycle and passively controls the channel selector valve bysaid motive power, therefore, upon a selector operation of a valve suchas a four-way selector valve provided in the refrigerating cycle forselecting a channel of fluid, prevention of environmental pollution andenergy saving and the like are effectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the control section controls atleast one of a plurality of functional components communicated to therefrigerating cycle so as to start an operation of the refrigeratingcycle, thereby controlling the channel selector valve in a statecorresponding to the start of an operation, which is commanded by theoperation command section, therefore, upon a selector operation of avalve such as a four-way selector valve provided in the refrigeratingcycle for selecting a channel of fluid, prevention of environmentalpollution and energy saving and the like are effectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the control section starts tooperate a compressor communicated to the refrigerating cycle in adirection of inverse rotation when the control section decides to selectthe channel selector valve on the basis of a command of the operationcommand section, thereby a channel is selected by the channel selectorvalve, therefore, upon a selector operation of a valve such as afour-way selector valve provided in the refrigerating cycle forselecting a channel of fluid, prevention of environmental pollution andenergy saving and the like are effectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the control section controls atleast one of a plurality of functional components communicated to therefrigerating cycle so as to operate the refrigerating cycle, therebycontrolling the channel selector valve in a state corresponding to theoperation, which is commanded by the operation command section,therefore, upon a selector operation of a valve such as a four-wayselector valve provided in the refrigerating cycle for selecting achannel of fluid, prevention of environmental pollution and energysaving and the like are effectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the control section controls atleast one of a plurality of functional components communicated to therefrigerating cycle so as to halt an operation of the refrigeratingcycle, thereby controlling the channel selector valve in a statecorresponding to the halt of the operation, which is commanded by theoperation command section, therefore, upon a selector operation of avalve such as a four-way selector valve provided in the refrigeratingcycle for selecting a channel of fluid, prevention of environmentalpollution and energy saving and the like are effectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the channel selector valve isconstructed in a manner that a movable member moves so as to select achannel, and the control section comprises at least one unit selectedfrom the group consisting of: a memory unit for memorizing position dataof the movable member of the channel selector valve; a comparison unitand a judge unit for comparing and judging, respectively, the positiondata and operation command data; and a learning unit learning on thebasis of physical quantity data by a control of functional componentsand control data of the channel selector valve, therefore, upon aselector operation of a valve such as a four-way selector valve providedin the refrigerating cycle for selecting a channel of fluid, preventionof environmental pollution and energy saving and the like areeffectively achieved, and in addition, a secure control of therefrigerating cycle can be performed.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the control section receives theinput signals, performs a predetermined processing and judges whether achannel is to be changed or not to be changed by the channel selectorvalve, then confirms a position on the basis of present position data,then sends the output signals to the driving section so as to controlthe functional components in the refrigerating cycle, then receives newinput signals after a predetermined period of time, confirms a positionof the movable member, and sets position data of said position as newpresent position data when said position is changed to a new position,therefore, upon a selector operation of a valve such as a four-wayselector valve provided in the refrigerating cycle for selecting achannel of fluid, prevention of environmental pollution and energysaving and the like are effectively achieved, and in addition, a securecontrol of the refrigerating cycle can be performed.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the control section confirms aposition of the movable member by at least one temperature detectionmeans, at least one pressure detection means, at least one magneticdetection means, at least one current detection means or a combinationthereof after a predetermined period of time, and then installs positiondata corresponding to said position into the memory unit of the controlsection, therefore, upon a selector operation of a valve such as afour-way selector valve provided in the refrigerating cycle forselecting a channel of fluid, prevention of environmental pollution andenergy saving and the like are effectively achieved, and in addition, asecure control of the refrigerating cycle can be performed.

According to a device for controlling a refrigerating cycle of thepresent invention as described above, a microcomputer that controls therefrigerating cycle is used, thereby controlling at least one of aplurality of functional components communicated to the refrigeratingcycle so as to control the refrigerating cycle, and in order to controlthe driving section for driving the functional component so that theposition of the movable member is to be moved or not to be moved, themicrocomputer performs a processing consisting of the steps of:

receiving input signals; confirming a position by taking out presentposition data of a movable member installed in a memory unit; carryingout an operation to decide whether the movable member is to be moved ofnot to be moved, comparing, and judging; selecting and deciding adriving section; outputting drive signals to the driving sectionselected and decided; judging a position of the movable member by inputsignals after a predetermined period of time, with or without moving aposition of the movable member by a physical quantity generated by atleast one functional component that is selected and decided in said stepof selecting and deciding or a rate of the physical quantity; andinstalling position data of a position of the movable member into thememory unit when said position is changed to a new position,

therefore, upon a selector operation of a valve such as a four-wayselector valve provided in the refrigerating cycle for selecting achannel of fluid, prevention of environmental pollution and energysaving and the like are effectively achieved, and in addition, a securecontrol of the refrigerating cycle can be performed.

According to a device for controlling a refrigerating cycle of thepresent invention as described above, an operational condition of therefrigerating cycle is commanded from an operation command section and aphysical quantity generated by the refrigerating cycle is detected in aphysical quantity detector section, then the control section receivesinput signals sent from the operation command section and the physicalquantity detector section. Then, the control section sends outputsignals to a driving section that drives a drive source of at least oneof a plurality of functional components communicated to therefrigerating cycle so as to control said functional component forcontrolling an operation of the refrigerating cycle, and when judging toselect a channel by using the channel selector valve on the basis of acommand of the operation command section, the control section sendsoutput signals to a driving section for driving a power source of acompressor so as to start an operation of the compressor of therefrigerating cycle and starts an operation of the refrigerant cycle soas to generate a motive power exceeding a first predetermined motivepower, thereby the channel selector valve is passively controlled.Therefore, upon a selector operation of a valve such as a four-wayselector valve provided in the refrigerating cycle for selecting achannel of fluid, prevention of environmental pollution and energysaving and the like are effectively achieved, and in addition, a securecontrol of the refrigerating cycle can be performed.

According to a device for controlling a refrigerating cycle of thepresent invention as described above, an operational condition of therefrigerating cycle is commanded from an operation command section and aphysical quantity generated by the refrigerating cycle is detected in aphysical quantity detector section, then the control section receivesinput signals sent from the operation command section and the physicalquantity detector section. Then, the control section sends outputsignals to a driving section that drives a drive source of at least oneof a plurality of functional components communicated to therefrigerating cycle so as to control said functional component forcontrolling an operation of the refrigerating cycle, and when judging toselect a channel by using the channel selector valve on the basis of acommand of the operation command section, the control section sendsoutput signals to a driving section for driving a power source of acompressor so as to start an operation of the compressor in a directionof inverse rotation and starts an operation of the refrigerant cycle soas to generate a motive power exceeding a third predetermined motivepower, thereby the channel selector valve is passively controlled.Therefore, upon a selector operation of a valve such as a four-wayselector valve provided in the refrigerating cycle for selecting achannel of fluid, prevention of environmental pollution and energysaving and the like are effectively achieved, and in addition, a securecontrol of the refrigerating cycle can be performed.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the channel selector valve selectsa channel by moving the movable member between the first and secondpositions in response to an internal motive power, the control sectionmemorizes position data corresponding to the first or second position ofthe movable member in a memory unit thereof, the control section startsan operation of the refrigerating cycle when the position data indicatesthe second or first position, halts the operation of the refrigeratingcycle with renewing position data in the memory unit to the first orsecond position, respectively, after a first predetermined period oftime, and keeps the operation of the refrigerating cycle standby duringa third predetermined period of time. Therefore, upon a selectoroperation of a valve such as a four-way selector valve provided in therefrigerating cycle for selecting a channel of fluid, prevention ofenvironmental pollution and energy saving and the like are effectivelyachieved, and in addition, a secure control of the refrigerating cyclecan be performed.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the control section operates thecompressor in a specific frequency immediately after starting theoperation of the compressor and starts an operation of the refrigeratingcycle so that a motive power exceeding a first predetermined motivepower is generated as an internal motive power of the channel selectorvalve. Therefore, upon a selector operation of a valve such as afour-way selector valve provided in the refrigerating cycle forselecting a channel of fluid, prevention of environmental pollution andenergy saving and the like are effectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the control section starts anoperation of the compressor with a first predetermined capacity,therefore, upon a selector operation of a valve such as a four-wayselector valve provided in the refrigerating cycle for selecting achannel of fluid, prevention of environmental pollution and energysaving and the like are effectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the device acts similarly to thedevice as described in claim 72, in addition,] the control sectionstarts an operation of the compressor with a second predeterminedcapacity so that a motive power lower than a first predetermined motivepower is generated as an internal motive power of the channel selectorvalve, then operates the refrigerating cycle for a fourth predeterminedperiod of time, then halts the operation of the refrigerating cycle fora fifth predetermined period of time, and then starts an operation ofthe compressor with a first predetermined capacity so that a motivepower exceeding a first predetermined motive power is generated as aninternal motive power of the channel selector valve. Therefore, upon aselector operation of a valve such as a four-way selector valve providedin the refrigerating cycle for selecting a channel of fluid, preventionof environmental pollution and energy saving and the like areeffectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the control section sends outputsignals to a throttle device driving section so that an opening ratio ofa throttle device of the refrigerating cycle is almost fully opened oralmost fully closed, therefore, upon a selector operation of a valvesuch as a four-way selector valve provided in the refrigerating cyclefor selecting a channel of fluid, prevention of environmental pollutionand energy saving and the like are effectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the control section sends outputsignals to a heat exchanger motor driving section so that a heatexchanger motor of the refrigerating cycle is kept halted, therefore,upon a selector operation of a valve such as a four-way selector valveprovided in the refrigerating cycle for selecting a channel of fluid,prevention of environmental pollution and energy saving and the like areeffectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, once the control section starts anoperation of the compressor, the control section sends output signals tothe compressor driving section after a first predetermined period oftime and drives the power source of the compressor so that a motivepower exceeding a second predetermined motive power is generated,thereby operating the refrigerating cycle. Therefore, upon a selectoroperation of a valve such as a four-way selector valve provided in therefrigerating cycle for selecting a channel of fluid, prevention ofenvironmental pollution and energy saving and the like are effectivelyachieved, and in addition, a secure control of the refrigerating cyclecan be performed.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, once the control section starts anoperation of the compressor, the control section sends output signals tothe throttle device driving section so as to set the opening ratio ofthe throttle device a predetermined opening ratio after a firstpredetermined period of time, therefore, upon a selector operation of avalve such as a four-way selector valve provided in the refrigeratingcycle for selecting a channel of fluid, prevention of environmentalpollution and energy saving and the like are effectively achieved, andin addition, a secure control of the refrigerating cycle can beperformed.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, once the control section starts anoperation of the compressor, the control section sends output signals tothe heat exchanger motor driving section after a second predeterminedperiod of time so as to start an operation of the heat exchanger motor,sends output signals to the compressor driving section so as to generatea motive power lower than a first predetermined motive power, and drivesthe power source of the compressor so as to generate a motive powerexceeding a second predetermined motive power, thereby operating therefrigerating cycle. Therefore, upon a selector operation of a valvesuch as a four-way selector valve provided in the refrigerating cyclefor selecting a channel of fluid, prevention of environmental pollutionand energy saving and the like are effectively achieved, and inaddition, a secure control of the refrigerating cycle can be performed.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, when the control section performsa predetermined processing and judges to select a channel by the channelselector valve or to halt an operation of the refrigerating cycle, thecontrol section sends output signals to the compressor driving section:to drive the power source of the compressor with a third predeterminedcapacity so as to generate a motive power lower than a secondpredetermined motive power; or to halt the operation of the compressor,thereby halting the operation of the refrigerating cycle. Therefore,upon a selector operation of a valve such as a four-way selector valveprovided in the refrigerating cycle for selecting a channel of fluid,prevention of environmental pollution and energy saving and the like areeffectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, when the control section performsa predetermined processing and judges to select a channel by the channelselector valve or to halt an operation of the refrigerating cycle, thecontrol section sends output signals to the compressor driving sectionto halt the operation of the compressor, then keeps the refrigeratingcycle standby for a third predetermined period of time, then sendsoutput signals to the compressor driving section to start the operationof the compressor, then renews position data in a memory unit to a firstor second position after a first predetermined period of time, therebyhalting the operation of the compressor again. Therefore, upon aselector operation of a valve such as a four-way selector valve providedin the refrigerating cycle for selecting a channel of fluid, preventionof environmental pollution and energy saving and the like areeffectively achieved, and in addition, a secure control of therefrigerating cycle can be performed.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, when positional data memorized bya memory unit of the control section indicate a first or secondposition, the control section starts an operation of the refrigeratingcycle so that a motive power exceeding a first predetermined motivepower is generated as an internal motive power of the channel selectorvalve. Therefore, upon a selector operation of a valve such as afour-way selector valve provided in the refrigerating cycle forselecting a channel of fluid, prevention of environmental pollution andenergy saving and the like are effectively achieved, and in addition, asecure control of the refrigerating cycle can be performed.

According to a device for controlling a refrigerating cycle of thepresent invention as described above, an operational condition of therefrigerating cycle is commanded from an operation command section and aphysical quantity generated by the refrigerating cycle is detected in aphysical quantity detector section, then the control section receivesinput signals sent from the operation command section and the physicalquantity detector section. Then, the control section sends outputsignals to a driving section that drives a drive source of at least oneof a plurality of functional components communicated to therefrigerating cycle so as to control said functional component forcontrolling an operation of the refrigerating cycle, and when judgingnot to select (i.e. not to switch) a channel by using the channelselector valve on the basis of a command of the operation commandsection, the control section sends output signals to a driving sectionfor driving a power source of a compressor so as to start an operationof the compressor of the refrigerating cycle and starts an operation ofthe refrigerant cycle so as to generate a motive power lower than afirst predetermined motive power, thereby the channel selector valve ispassively controlled. Therefore, upon a selector operation of a valvesuch as a four-way selector valve provided in the refrigerating cyclefor selecting a channel of fluid, prevention of environmental pollutionand energy saving and the like are effectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, the control section starts anoperation of the compressor with a second predetermined capacity,therefore, upon a selector operation of a valve such as a four-wayselector valve provided in the refrigerating cycle for selecting achannel of fluid, prevention of environmental pollution and energysaving and the like are effectively achieved.

According to a device for controlling a refrigerating cycle of thepresent invention as described above, an operational condition of therefrigerating cycle is commanded from an operation command section and aphysical quantity generated by the refrigerating cycle is detected in aphysical quantity detector section, then the control section receivesinput signals sent from the operation command section and the physicalquantity detector section. Then, the control section sends outputsignals to a driving section that drives a drive source of at least oneof a plurality of functional components communicated to therefrigerating cycle so as to control said functional component forcontrolling an operation of the refrigerating cycle, and when judgingnot to select (i.e. not to switch) a channel by using the channelselector valve on the basis of a command of the operation commandsection, the control section sends output signals to a driving sectionfor driving a power source of a compressor so as to start an operationof the compressor of the refrigerating cycle and starts an operation ofthe refrigerant cycle so as to generate a motive power exceeding a firstpredetermined motive power, thereby the channel selector valve ispassively controlled. Therefore, upon a selector operation of a valvesuch as a four-way selector valve provided in the refrigerating cyclefor selecting a channel of fluid, prevention of environmental pollutionand energy saving and the like are effectively achieved.

According to the device for controlling a refrigerating cycle of thepresent invention as described above, when the control section performsa predetermined processing and judges to halt an operation of therefrigerating cycle, the control section sends output signals to thecompressor driving section so as to halt the operation of thecompressor, then keeps the refrigerating cycle standby for a thirdpredetermined period of time without renewing position data in a memoryunit. Therefore, upon a selector operation of a valve such as a four-wayselector valve provided in the refrigerating cycle for selecting achannel of fluid, prevention of environmental pollution and energysaving and the like are effectively achieved, and in addition, a securecontrol of the refrigerating cycle can be performed.

What is claimed is:
 1. A channel selector valve for selecting a channelof fluid comprising: a movable member moving between a first positionand a second position in a housing of the channel selector valve; anddriving means for driving the movable member between the first positionand the second position by employing non-electric motive power generatedwhen a control section controls a physical quantity of the fluid,wherein a first selector port out of two selector ports of the housingcommunicates with a main port of the housing through the interior of thehousing when the movable member is situated at the first position, whilea second selector port out of the two selector ports of the housingcommunicates with a main port of the housing through the interior of thehousing when the movable member is situated at the second position. 2.The channel selector valve according to claim 1, wherein a drive sourcegenerating said non-electric motive power comprises at least one ofelement components in a refrigerating cycle having the channel selectorvalve, a change in physical quantity, which arises in the refrigeratingcycle from an action of said at least one of element components, isemployed as at least a part of said motive power, thereby the channel ispassively selected.
 3. The channel selector valve according to claim 2,wherein said change in physical quantity is at least one change amongchanges in pressure, differential pressure and flow rate of fluid in thechannel selector valve, said changes arising from an action of said atleast one of the element components.
 4. The channel selector valveaccording to claim 2, wherein the element component is an electricallydriven expansion valve provided in the refrigerating cycle and thechange in physical quantity is a change in pressure of fluid due to achange in an opening ratio of the electrically driven expansion valve.5. The channel selector valve according to claim 2, wherein the elementcomponent is a compressor provided in the refrigerating cycle and thechange in physical quantity is a change in a frequency of a mechanicaloscillation generated by the compressor.
 6. The channel selector valveaccording to claim 2, wherein the element component is a heat exchangerprovided in the refrigerating cycle and the change in physical quantityis a change in pressure of fluid due to a change in the amount of heatexchange by the heat exchanger.
 7. A channel selector valve constitutedas a four-way selector valve by combining a first and second three-wayselector valves, each of which is constituted by the channel selectorvalve according to claim
 1. 8. The channel selector valve according toclaim 7, wherein the channel selector valve is constituted as a four-wayselector valve by the first and second three-way selector valves, themain port of the first three-way selector valve is an inlet port formedin the housing, through which fluid introduced from the exterior to theinterior of the housing of the first three-way selector valve passes,while the main port of the second three-way selector valve is an outletport formed in the housing, through which the fluid discharged from theinterior to the exterior of the housing of the second three-way selectorvalve passes, the first selector port of the first three-way selectorvalve is connected to the second selector port of the second three-wayselector valve, while the second selector port of the first three-wayselector valve is connected to the first selector port of the secondthree-way selector valve, the movable member of the second three-wayselector valve moves to the second position when the movable member ofthe first three-way selector valve moves to the first position, whilethe movable member of the second three-way selector valve moves to thefirst position when the movable member of the first three-way selectorvalve moves to the second position.
 9. The channel selector valveaccording to claim 8, wherein said driving means of the first three-wayselector valve comprises: a first drive mechanism that moves the movablemember situated at the first position of the first three-way selectorvalve to the second position when a difference between a fluid pressureat the first selector port in the first three-way selector valve and afluid pressure at the second selector port cancels out; and a seconddrive mechanism that moves the movable member situated at the secondposition of the first three-way selector valve to the first positionwhen a difference between a fluid pressure at the first selector port inthe first three-way selector valve and a fluid pressure at the secondselector port cancels out.
 10. The channel selector valve according toclaim 9, wherein the first and second three-way selector valves areconstructed so that the main port is isolated from the second selectorport when the movable member is situated between the first position anda third position where is nearer to the second position than the firstposition, while that the main port is isolated from the first selectorport when the movable member is situated between the second position anda fourth position where is between the second position and the thirdposition, the first drive mechanism comprises first storing means forstoring energizing force to move the movable member of the firstthree-way selector valve from the first position to the fourth position,by a fluid pressure being higher than a first predetermined value of themain port, when the movable member of the first three-way selector valveis situated at the first position, said energizing force being less thanthe first predetermined value, and the second drive mechanism comprisessecond storing means for storing energizing force to move the movablemember of the first three-way selector valve from the second position tothe third position, by a fluid pressure being higher than a secondpredetermined value of the main port, when the movable member of thefirst three-way selector valve is situated at the second position, saidenergizing force being less than the second predetermined value.
 11. Thechannel selector valve according to claims 1, 2 or 3 wherein the mainport is an inlet port formed in the housing, through which fluidintroduced from the exterior to the interior of the housing passes, thehousing further comprises an outlet port, through which the fluiddischarged from the interior to the exterior of the housing passes, whenthe movable member is situated at the first position, the inlet port andthe first selector port are communicated with each other inside thehousing, while the outlet port and the second selector port arecommunicated with each other inside the housing, when the movable memberis situated at the second position, the inlet port and the secondselector port are communicated with each other inside the housing, whilethe outlet port and the first selector port are communicated with eachother inside the housing.
 12. The channel selector valve according toclaim 11, wherein the movable member partitions the interior of thehousing into a first and second pressure chambers and also forms a firstand second spaces in the first pressure chamber, the inlet port isformed in the housing so as to communicate with the first space and theoutlet port is formed in the housing so as to communicate with thesecond space, when the movable member is situated at the first position,the fluid introduced from the exterior of the housing into the firstspace by way of the inlet port is discharged to the first selector port,while the fluid discharged from the second space to the exterior of thehousing by way of the outlet port is introduced from the second selectorport, when the movable member is situated at the second position, thefluid introduced from the exterior of the housing into the first spaceby way of the inlet port is discharged to the second selector port,while the fluid discharged from the second space to the exterior of thehousing by way of the outlet port is introduced from the first selectorport.
 13. A compressor with the channel selector valve as claimed inclaim 12 comprising: a compressor housing having an inlet, which isconnected to the outlet port; a low pressure chamber that is provided inthe interior of the compressor housing and communicates with the inlet;a high pressure chamber that is provided in the interior of thecompressor housing and partitioned off from the low pressure chamber;and a compressing section that is provided in the interior of thecompressor housing, compresses fluid introduced into the low pressurechamber from the inlet, and guides the fluid into the high pressurechamber, wherein a part of the compressor housing partitioning the highpressure housing therein is integrally formed with a part of the housinghaving the inlet port therein, thereby the interior of the part of thehousing communicates with the high pressure chamber.
 14. A method ofdriving the channel selector valve as claimed in claim 12, comprisingthe steps of: communicating the first space to the second pressurechamber through an equalizing path formed in the movable member;energizing the movable member in a direction of moving from the secondposition to the first position by energizing means for energizing; andapplying a force to the movable member from the first pressure chamberside by fluid introduced from the exterior of the housing into the firstspace by way of the inlet port, said force being stronger than aresultant force consisting of an energizing force by said energizingmeans and a force applied to the movable member by fluid in the secondpressure chamber introduced from the first space by way of saidequalizing path, thereby the movable member moves from the firstposition to the second position.
 15. The channel selector valveaccording to claim 12, wherein the housing has a valve seat disposed inthe first pressure chamber, the outlet port and the two selector portsare disposed on the valve seat, the second space moves on the valve seatresponding to a movement of the movable member moving between the firstand second positions, and a place with which the outlet portcommunicates by way of the second space is selected to be either thefirst selector port or the second selector port.
 16. A method of drivingthe channel selector valve as claimed in claim 15, comprising the stepsof: communicating the first space to the second pressure chamber throughan equalizing path formed in the movable member; energizing the movablemember in a direction of moving from the second position to the firstposition by energizing means for energizing; and applying a force to themovable member from the first pressure chamber side by fluid introducedfrom the exterior of the housing into the first space by way of theinlet port, said force being stronger than a resultant force consistingof an energizing force by said energizing means, a force applied to themovable -member by fluid in the second pressure chamber introduced fromthe first space by way of said equalizing path, and a static frictionforce between the valve seat and the movable member, whereby the movablemember moves from the first position to the second position and themovable member is kept staying at the second position by the staticfriction force between the valve seat and the movable member against anenergizing force of the energizing means, after a difference between apressure of fluid in the first space and that in the second pressurechamber decreases due to circulation of fluid between the first spaceand the second pressure chamber through the equalizing path.
 17. Thechannel selector valve according to claim 12, wherein the driving meanscomprises: a third drive mechanism that moves the movable member fromone position out of the first and second positions toward an oppositeposition; and a fourth drive mechanism that moves the movable memberfrom the opposite position toward the one position, wherein the thirdand fourth drive mechanisms employ a change in physical quantity of theinterior of the housing due to fluid introduced into the interior of thehousing at least as a part of the motive power.
 18. The channel selectorvalve according to claim 17, wherein the movable member partitions theinterior of the housing into the first pressure chamber, the secondpressure chamber, and a third pressure chamber situated so that thefirst pressure chamber is sandwiched between the second and thirdpressure chambers, the channel selector valve further comprises anon-electrically driven pilot valve that selectively communicates theoutlet port to either the second pressure chamber or the third pressurechamber, said pilot valve comprises: a second housing having a secondmain port that is provided outside the housing and communicates with theoutlet port; and a selector valve element that partitions the interiorof the second housing into a fourth pressure chamber communicating withthe third pressure chamber and a fifth pressure chamber communicatingwith the second pressure chamber, and that is movable in the secondhousing between a fifth position where the second main port communicateswith the fourth pressure chamber and a sixth position where the secondmain port communicates with the fifth pressure chamber, due to adifference between a pressure of fluid in the second pressure chamberand that in the third pressure chamber.
 19. The channel selector valveaccording to claim 18, further comprising second driving means to movethe selector valve element from one position out of the fifth and sixthpositions to an opposite position when the difference between a pressureof fluid in the second pressure chamber and that in the third pressurechamber cancels out.
 20. The channel selector valve according to claim19, wherein the movable member has a first equalizing path communicatingthe first space to the second pressure chamber and a second equalizingpath communicating the first space to the third pressure chamber, themovable member has a first subvalve that isolates the third pressurechamber from the fourth pressure chamber when the movable member issituated at the first position and that communicates the third pressurechamber to the fourth pressure chamber when the movable member issituated at the second position, and has a second subvalve thatcommunicates the second pressure chamber to the fifth pressure chamberwhen the movable member is situated at the first position and thatisolates the second pressure chamber from the fifth pressure chamberwhen the movable member is situated at the second position, the pilotvalve communicates the second main port to the fourth pressure chamberwhen the selector valve element is situated between the fifth positionand a seventh position located nearer to the sixth position than thefifth position, and communicates the second main port to the fifthpressure chamber when the selector valve element is situated between thesixth position and a eighth position located between the sixth positionand the seventh position, and the second driving means has third andfourth storing means for storing energizing force, the third storingmeans for storing energizing force stores an energizing force, which isless than a third predetermined value, to move the selector valveelement from the fifth position to the eighth position due to a fluidpressure in the fifth pressure chamber exceeding the third predeterminedvalue when the selector valve element is situated at the fifth position,and the fourth storing means for storing energizing force stores anenergizing force, which is less than a fourth predetermined value, tomove the selector valve element from the sixth position to the seventhposition due to a fluid pressure in the fourth pressure chamberexceeding the fourth predetermined value when the selector valve elementis situated at the sixth position.
 21. The channel selector valveaccording to claim 18, wherein a third main port communicating with theinlet port is further formed in the second housing, the third main portcommunicates with the fifth pressure chamber when the selector valveelement is situated between the fifth and seventh positions andcommunicates with the fourth pressure chamber when the selector valveelement is situated between the sixth and eighth positions, and thechannel selector valve further comprises second driving means for movingthe selector valve element either from the fifth position to the eighthposition or from the sixth position to the seventh position when thedifference between a pressure of fluid in the second pressure chamberand that in the third pressure chamber cancels out.
 22. The channelselector valve according to claim 21, wherein the second driving meanshas third and fourth storing means for storing energizing force, thethird storing means for storing energizing force stores an energizingforce, which is less than a third predetermined value, to move theselector valve element from the fifth position to the eighth positiondue to a fluid pressure in the fifth pressure chamber exceeding thethird predetermined value when the selector valve element is situated atthe fifth position, and the fourth storing means for storing energizingforce stores an energizing force, which is less than a fourthpredetermined value, to move the selector valve element from the sixthposition to the seventh position due to a fluid pressure in the fourthpressure chamber exceeding the fourth predetermined value when theselector valve element is situated at the sixth position.
 23. Thechannel selector valve according to claim 12, wherein the driving meanscomprises: a third drive mechanism to move the movable member from oneposition out of the first and second positions to an opposite position;and a fourth drive mechanism to move the movable member from theopposite position to the one position, wherein one drive mechanism outof the third and fourth drive mechanisms employs a change in physicalquantity of the interior of the housing due to fluid introduced into theinterior of the housing at least as a part of the motive power, while anopposite drive mechanism employs an energizing force that is applied tothe movable member by energizing means received in the interior of thehousing at least as a part of the motive power.
 24. The channel selectorvalve according to claim 23, further comprising a latch mechanism thatselectively controls a movement of the movable member from one positionout of the first and second positions toward an opposite position. 25.The channel selector valve according to claim 24, wherein the latchmechanism selectively performs a first and second states, in the firststate, a movement of the movable member to the opposite position by thedriving means is controlled at the first position, and in the secondstate, a movement of the movable member from the one position to theopposite position by the driving means is allowed.
 26. The channelselector valve according to claim 25, wherein the latch mechanismcomprises a latch piece that moves in the housing following a movementof the movable member between the first and second positions, and in afirst state of the latch mechanism, a movement of the latch piece iscontrolled, thereby a movement of the movable member is controlled atthe one position.
 27. A method of driving the channel selector valve asclaimed in claim 25, wherein when the movable member, a movement ofwhich to the opposite position is controlled by the latch mechanism andsituated at the one position, is moved to the opposite position, themovable member is once moved by the driving means in a direction ofmoving from the opposite position to the one position, then is movedfrom the one position to the opposite position, and when the movablemember situated at the opposite position is moved to the one position,the movable member is once moved by the driving means in a direction ofmoving from the one position to the opposite position, then is movedfrom the opposite position to the one position.
 28. The channel selectorvalve according to claim 23, further comprising: a valve-opening memberthat moves from a valve-closing position to a valve-opening position bythe motive power while the third drive mechanism generates the motivepower; a pilot path that is opened from a valve closing state thereof bythe valve-opening member moved from the valve-closing position to thevalve-opening position; an attenuation mechanism acting when the pilotpath is open, which attenuates the motive power generated by the fourthdrive mechanism so as to prevent the movable member from moving from theopposite position to the one position; and a second latch mechanism toselectively control a movement of the valve-opening member from thevalve-closing position to the valve opening position.
 29. The channelselector valve according to claim 28, wherein the second latch mechanismalternately repeats a third and fourth states, in the third state, amovement of the valve-opening member to the valve-opening position iscontrolled at the valve-closing position, and in the fourth state, amovement of the valve-opening member from the valve-closing position tothe valve-opening position is allowed.
 30. A method of driving thechannel selector valve as claimed in claim 28, wherein when the movablemember situated at the one position is moved to the opposite position, ageneration of the motive power by the third drive mechanism is oncehalted, then the generation thereof by the third drive mechanism isstarted again and then, the motive power generated by the third drivemechanism is maintained to be a predetermined value exceeding the motivepower, which is generated by the fourth drive mechanism and attenuatedby the attenuation mechanism, and when the movable member situated atthe opposite position is moved to the one position, a generation of themotive power by the third drive mechanism is halted, then the movablemember is moved from the opposite position to the one position by thefourth drive mechanism.
 31. The channel selector valve according toclaim 23, wherein the driving means comprises a communication pipe thatalways communicates the second pressure chamber to the first selectorport outside the housing.
 32. The channel selector valve according toclaim 23, wherein the driving means comprises a state-holding mechanismto hold the movable member, which is moved from the first position tothe second position, at the second position.
 33. The channel selectorvalve according to claim 32, wherein the state-holding mechanismcomprises: a state-holding selector valve provided in the secondpressure chamber, which by a selecting action of a second selector valveelement selects either a first state or a second state, in said firststate the second pressure chamber communicates with the exterior of thehousing through a first introducing port and in said second state thesecond pressure chamber communicates with the exterior of the housingthrough a second introducing port; and energizing means for energizingthe selector valve, which energizes the second selector valve element sothat the state-holding selector valve in the second state selects thefirst state, the movable member allows the energizing means forenergizing the selector valve to energize the second selector valveelement when the movable member is situated at the first position, whilethe movable member makes the second selector valve element act aselection so that the state-holding selector valve selects the secondstate against an energizing by the energizing means for energizing theselector valve when the movable member is situated at the secondposition.
 34. The channel selector valve according to claim 33, whereinthe energizing means energizes the movable member in a direction ofmoving from the second position to the first position, and a pressure offluid, which is introduced from the exterior of the housing into thefirst space by way of the inlet port, acts on the movable member in adirection of moving from the first position to the second position. 35.A method of driving the channel selector valve as claimed in claim 34,wherein when the movable member moves from the first position to thesecond position, a pressure of fluid introduced into the first spacefrom the exterior of the housing by way of the inlet port is set higherthan a predetermined value, so that a force, which is applied to themovable member by fluid existing in the first space in a direction fromthe first position to the second position, is set stronger than a force,which is applied to the movable member by fluid existing in the place towhich the second pressure chamber is communicated in a direction fromthe second position to the first position, after the movable member hasmoved from the first position to the second position, a pressure offluid existing in the first space and a pressure of fluid existing inthe second pressure chamber are set so that the movable member is keptstaying at the second position.
 36. The channel selector valve accordingto claim 11, wherein the housing is formed cylindrical, at least the twoselector ports are formed at a valve seat situated at one end of thehousing in a direction of a central axis of the housing, the movablemember is constructed by a main valve element, which is received in thehousing and rotative around the central axis, the main valve element isprovided with communication means for selectively communicating aselector port out of the two selector ports to the main port, the mainvalve element rotates and displaces around the central axis so as tomove between the first and second positions, when the main valve elementis situated at the first position, a first selector port out of the twoselector ports is communicated to the main port by the communicationmeans, and when the main valve element is situated at the secondposition, a second selector port out of the two selector ports iscommunicated to the main port by the communication means.
 37. Thechannel selector valve according to claim 36, wherein at least one portout of the inlet port and the outlet port is formed at the valve seat,an end surface of the main valve element in a direction of the centralaxis sits down on the valve seat, said end surface is provided withsecond communication means for selectively communicating said one portto a first selector port out of the two selector ports, when the mainvalve element is situated at the first position, the secondcommunication means communicates the second selector port to said oneport, and when the main valve element is situated at the secondposition, the second communication means communicates the first selectorport to said one port.
 38. The channel selector valve according to claim37, wherein the opposite port is formed at an opposite end of thehousing in a direction of the central axis, and the communication meanshas a communication channel that communicates one end surface side ofthe main valve element to an opposite end surface side of the main valveelement in the interior of the housing.
 39. The channel selector valveaccording to claim 36, further comprising conversion means forconverting a moving direction, which converts a movement of the mainvalve element in a direction of the central axis with respect to thehousing into a movement in a rotational direction around the centralaxis, wherein the main valve element is movable in a direction of thecentral axis in the interior of the housing, and the driving means makesthe main valve element have a reciprocating motion in a direction of thecentral axis with respect to the housing.
 40. The channel selector valveaccording to claim 39, wherein the conversion means for converting amoving direction comprises: a cam groove that is provided in one out ofthe main valve element and the housing, and extends over a wholecircumference of the rotational direction; and a cam follower pin thatis provided in another out of the main valve element and the housing,and moves in the cam groove, the cam groove has a first and second camgrooves continuing with each other in the rotational direction, saidfirst cam groove is formed inclined so as to part from the valve seat ina direction of the central axis as being displaced in the rotationaldirection, while said second cam groove is formed inclined so as to movenearer to the valve seat in a direction of the central axis as beingdisplaced in the rotational direction.
 41. The channel selector valveaccording to claim 40, wherein the cam groove is provided in thehousing, the housing comprises an outer housing and an inner housingreceived in the outer housing, the inner housing comprises a first halfand a second half divided in a direction of the central axis in a statethat the inner housing is received in the outer housing, and each guide,which constitutes the cam groove in a state that an end of the firsthalf and an end of the second half are joined with each other, is formedat the respective ends of the first and second halves.
 42. The channelselector valve according to claim 40, wherein at least one port out ofthe inlet port and the outlet port is formed at the valve seat, secondcommunication means is formed at an end surface of the main valveelement, the end surface faces the valve seat, said second communicationmeans selectively communicates the opposite port to a first selectorport out of the two selector ports in a state that the end surface sitsdown on the valve seat, when the main valve element is situated at thefirst position, the second selector port is communicated to the oppositeport by the second communication means of the main valve element, andthe end surface of which sits down on the valve seat, and when the mainvalve element is situated at the second position, the first selectorport is communicated to the opposite port by the second communicationmeans of the main valve element, and the end surface of which sits downon the valve seat.
 43. The channel selector valve according to claim 42,wherein the opposite port is formed at an opposite end side of thehousing in a direction of the central axis, and the communication meanscomprises: a communication channel that communicates one end surfaceside of the main valve element to an opposite end surface side of themain valve element in the housing; a subvalve that opens and closes thecommunication channel; subvalve energizing means for energizing thesubvalve toward a direction of closing; and valve opening means foropening the subvalve against an energizing force by the subvalveenergizing means in a state that the one end surface of the main valveelement sits down on the valve seat.
 44. The channel selector valveaccording to claim 43, wherein the housing is disposed so that theopposite end of the housing is situated lower than one end of thehousing in a direction of the central axis, and the driving meansemploys an own weight of the main valve element at least as a part ofthe motive power.
 45. The channel selector valve according to claim 43,wherein the driving means employs an energizing force by energizingmeans for energizing main valve element, which energizes the main valveelement to part from the valve seat in a direction of the central axis,as a part of the motive power.
 46. The channel selector valve accordingto claim 43, wherein the driving means comprises second energizing meansfor energizing the main valve element, which energizes the main valveelement to move nearer to the valve seat in a direction of the centralaxis.
 47. The channel selector valve according to claim 46, wherein thedriving means comprises energizing means for energizing the main valveelement, which energizes the main valve element to part from the valveseat in a direction of the central axis, due to a resultant force of anenergizing force by the energizing means for energizing the main valveelement and an energizing force by the second energizing means forenergizing the main valve element, the cam follower pin is situated atan intermediate position of the cam groove except end portions of oneend side and an opposite end side of the housing in a direction of thecentral axis, and the main valve element is situated at a neutralposition halfway within a reciprocating motion in a direction of thecentral axis when the cam follower pin is situated at the intermediateposition.
 48. The channel selector valve according to claim 47, whereinan end portion of the one end side of the housing in a direction of thecentral axis out of the cam groove is provided with a groove thatcontinues to a join, at which one end of the first cam groove beingsituated at the one end side of the housing is connected to one end ofthe second cam groove, the groove is formed so that the one end surfaceof the main valve element sits down on the valve seat in a state thatthe cam follower pin is situated at the groove, the groove is disposedbeing displaced to the lower course than the the groove is formed sothat the one end surface of the main valve element sits down on thevalve seat in a state that the cam follower pin is situated at thegroove, the groove is disposed being displaced to the lower course thanthe join in the rotational direction, and when the main valve elementmoves in the direction away from the valve seat in a direction of thecentral axis, a movement of the cam follower pin is controlled from thegroove to a cam groove out of the first and second cam grooves, which issituated at the upper course than the groove in the rotationaldirection.
 49. The channel selector valve according to claim 48, whereinan end portion of the opposite end side of the housing in a direction ofthe central axis out of the cam groove is provided with a second groovethat continues to a join, at which an opposite end of the first camgroove being situated at the opposite end side of the housing isconnected to an opposite end of the second cam groove, the second grooveis formed so that the main valve element is the farthest away from thevalve seat in a state that the cam follower pin is situated at thesecond groove, the second groove is disposed being displaced to thelower course than the second join in the rotational direction, and whenthe main valve element moves in the direction nearer to the valve seatin a direction of the central axis, a movement of the cam follower pinis controlled from the second groove to a cam groove out of the firstand second cam grooves, which is situated at the upper course than thesecond groove in the rotational direction.
 50. The channel selectorvalve according to claim 47, wherein an end portion of the opposite endside of the housing in a direction of the central axis out of the camgroove is provided with a second groove that continues to a join, atwhich an opposite end of the first cam groove being situated at theopposite end side of the housing is connected to an opposite end of thesecond cam groove, the second groove is formed so that the main valveelement is the farthest away from the valve seat in a state that the camfollower pin is situated at the second groove, the second groove isdisposed being displaced to the lower course than the second join in therotational direction, and when the main valve element moves in thedirection nearer to the valve seat in a direction of the central axis, amovement of the cam follower pin is controlled from the second groove toa cam groove out of the first and second cam grooves, which is situatedat the upper course than the second groove in the rotational direction.51. The channel selector valve as claimed in claim 36, wherein slidemeans for decreasing a sliding resistance between the housing and themain valve element is provided there between.
 52. A compressor with thechannel selector valve as claimed in claim 36 comprising: a compressorhousing having an inlet, which is connected to the outlet port; a lowpressure chamber that is provided in the interior of the compressorhousing and communicates with the inlet; a high pressure chamber that isprovided in the interior of the compressor housing and partitioned offfrom the low pressure chamber; and a compressing section that isprovided in the interior of the compressor housing, compresses fluidintroduced into the low pressure chamber from the inlet, and guides thefluid into the high pressure chamber, wherein a part of the compressorhousing partitioning the high pressure housing therein is integrallyformed with a part of the housing having the inlet port therein, therebythe interior of the part of the housing communicates with the highpressure chamber.